Systems and Methods Implementing Robust Air Conditioning Systems Configured to Utilize Thermal Energy Storage to Maintain a Low Temperature for a Target Space

ABSTRACT

Systems and methods in accordance with embodiments of the invention implement air conditioning systems that are operable to establish/maintain a desired temperature for a target space and simultaneously establish/maintain a temperature lower than the desired temperature for the target space for an included cold thermal energy storage unit. In one embodiment, an air conditioning system includes: a condensing unit; a liquid pressurizer and distributor ensemble; a cold thermal energy storage unit; a target space; and a suction gas/equalizer; where the listed components are operatively connected by piping such that vapor compression cycles can be simultaneously implemented that result in the cooling of the cold thermal energy storage unit and the target space; and the air conditioning system is configured such that the simultaneous implementation of vapor compression cycles results in cooling the cold thermal energy storage unit to a greater extent relative to the target space.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a continuation of U.S. application Ser. No.14/859,262 entitled “Systems and Methods Implementing Robust AirConditioning Systems Configured to Utilize Thermal Energy Storage toMaintain a Low Temperature for a Target Space,” filed Sep. 19, 2015,which application claims priority to: U.S. provisional patentapplication Ser. No. 62/052,999 entitled “Method for Shifting theElectricity Load of a Centralized Refrigeration System Using a ThermalEnergy Storage Apparatus to Condense and Prepare Refrigerant for DirectUse by Said or Auxiliary Refrigeration Systems,” filed on Sep. 19, 2014;U.S. provisional patent application Ser. No. 62/081,517 entitled “Methodfor Shifting the Electricity Load of a Centralized Refrigeration SystemUsing a Thermal Energy Storage Apparatus to Condense and PrepareRefrigerant for Direct Use by Said or Auxiliary Refrigeration Systems,”filed on Nov. 18, 2014; and, U.S. provisional patent application Ser.No. 62/165,026 entitled “Method for Shifting the Electricity Load of aCentralized Direct Expansion Cooling System Using a Thermal EnergyStorage Apparatus to Condense and Prepare Refrigerant for Direct Use bySaid or Auxiliary Direct Expansion Cooling Systems,” filed on May 21,2015, all of which are incorporated by reference herein in theirentirety.

FIELD OF THE INVENTION

The present invention generally relates to air conditioning systems thatimplement thermal energy storage devices.

BACKGROUND

Air conditioning is a convenience that is ubiquitous in modern society.Within the context of the instant application, ‘air conditioning’ can beunderstood to refer to the controlling of the properties ofair—especially temperature—within a defined space, and is inclusive ofboth the heating and cooling of air (although note that ‘airconditioning’ is sometimes colloquially interpreted not to refer toheating—i.e. heating is sometimes colloquially understood to be separatefrom air conditioning). Air conditioning can be implemented using any ofa variety of devices, and is typically used, for instance, to helpcreate comfortable indoor environments. Importantly, one criticalapplication for air conditioning is refrigeration, which is generallyused to preserve/elongate the shelf life of foods. Typical airconditioning systems—including refrigerators—employ a‘vapor-compression’ cycle to cool a targeted space. In a‘vapor-compression’ cycle, a working fluid (e.g. a refrigerant) iscirculated proximate the targeted space that is to be cooled, and ismade to undergo iterative phase changes to continually remove heat fromthe targeted space and eject it outside of the targeted space.

Vapor-compression cycles are typically implemented via a compressor, anexpansion valve, an evaporator, and a condenser, all operativelyconnected via piping that facilitates the circulation of a workingfluid. Typically, the working fluid—in its liquid phase—is made to passthrough the expansion valve and thereby experiences a pressure drop, anda corresponding temperature drop. The working fluid—typically then in asaturated fluid phase—subsequently passes through the evaporator, whichis the target of the cooling efforts. This saturated fluid absorbs heatfrom the evaporator, and consequently is made to substantially evaporateinto a vapor phase. The substantially vapor phase working fluid thenpasses through a compressor where it is compressed to a higher pressure,and relatedly a higher temperature. Thereafter, the high pressure, hightemperature vapor phase working fluid passes through a condenser, whereit releases heat outside of the evaporator and thereby condenses into aliquid phase working fluid, which can be re-circulated. Accordingly, itis enumerated how vapor-compression cycles are generally implemented toremove heat from a targeted space.

SUMMARY OF THE INVENTION

Systems and methods in accordance with embodiments of the inventionimplement air conditioning systems that are operable toestablish/maintain a desired temperature for a target space andsimultaneously establish/maintain a temperature lower than the desiredtemperature for the target space for an included cold thermal energystorage unit, such that the cold thermal energy storage unit cansubsequently be used to establish/maintain a desired temperature for thetarget space without having to principally rely on the operation of apowered condensing unit. In one embodiment, an air conditioning systemincludes: a condensing unit; a liquid pressurizer and distributorensemble; a cold thermal energy storage unit; a target space; and asuction gas pressurizer and distributor ensemble; where: the condensingunit, the liquid pressurizer and distributor ensemble, the cold thermalenergy storage unit, the target space, and the suction gas pressurizerand distributer ensemble are operatively connected by piping such thatvapor compression cycles can be simultaneously implemented that resultin the cooling of the cold thermal energy storage unit and the targetspace; and the air conditioning system is configured such that when thevapor compression cycles are simultaneously implemented that result inthe cooling of the cold thermal energy storage unit and the targetspace, the cold thermal energy storage unit cools to a greater extentthan the target space.

In another embodiment, the cold thermal energy storage unit includes afirst expansion device; the target space includes a second expansiondevice; and the first expansion device is operable to reduce thetemperature of received working fluid to a greater extent than thesecond expansion device.

In yet another embodiment, the suction gas pressurizer and distributorensemble includes: at least one of: a pressure regulator and acompressor; and a flow control apparatus operable to controllably directvapor phase working fluid to adjoined structures.

In still another embodiment, the cold thermal energy storage unitincludes a phase change material encased in thermal insulation.

In still yet another embodiment, the condensing unit includes acompressor and condenser in series, and where the condensing unit isoperable to direct received vapor phase working fluid through acompressor to compress the vapor phase working fluid, and then directthe compressed vapor phase working fluid through a condenser to condensethe vapor phase working fluid, such that the condensing unit can outputthe corresponding liquid phase working fluid.

In a further embodiment, the liquid pressurizer and distributor ensembleincludes a pump that is operable to alter the pressure of receivedliquid phase working fluid, and a flow control apparatus operable tocontrollably direct received liquid phase working fluid to adjoinedstructures.

In a still further embodiment, the condensing unit is operable to outputheated vapor phase working fluid.

In a yet further embodiment, the condensing unit includes an integratedheating source and is thereby operable to output heated vapor phaseworking fluid.

In a still yet further embodiment, the integrated heating source is agas powered heater.

In another embodiment, an air conditioning system further includespiping configured to direct heated vapor phase working fluid that isoutput by the condensing unit to the target space.

In yet another embodiment, the condensing unit is configured to outputheated vapor phase working fluid such that when the heated vapor phaseworking fluid is directed by the piping to the target space, itcondenses into a liquid phase working fluid.

In still another embodiment, an air conditioning system furtherincludes: a discharge gas distributor; and a hot thermal energy storageunit; where the discharge gas distributor, the hot thermal energystorage unit, the liquid pressurizer and distributor ensemble, and thetarget space are operatively connected by piping such that heated vaporphase working fluid output by the condensing unit can be circulated,using the discharge gas distributor, to the target space and/or the hotthermal energy storage unit.

In a further embodiment, the condensing unit is configured to outputheated vapor phase working fluid such that when the heated vapor phaseworking fluid is directed by piping to the target space and/or the hotthermal energy storage unit, it condenses into a liquid phase workingfluid.

In a yet further embodiment, the hot thermal energy storage unitincludes a thermal storage medium encased in thermal insulation.

In a still further embodiment, an air conditioning system furtherincludes: a second condensing unit; a second liquid pressurizer anddistributor ensemble; a second target space; a second discharge gasdistributor; and a condenser; where: the condensing unit and the secondcondensing unit are operatively connected by piping to the condenser;the second condensing unit, the second liquid pressurizer anddistributor ensemble, the second target space, and the cold thermalenergy storage unit are operatively connected by piping such that vaporcompression cycles can be simultaneously implemented that result in thecooling of the cold thermal energy storage unit and the target space;and the second condensing unit, the second discharge gas distributor,the second target space, and the hot thermal energy storage unit areoperatively connected by piping such that a working fluid can be heatedand circulated through the target space to heat it.

In a still yet further embodiment, an air conditioning system furtherincludes: a hot thermal energy storage unit that is operable to act as aheat source; where: the hot thermal energy storage unit and the targetspace are operatively connected by piping; and the hot thermal energystorage unit is configured to receive liquid phase working fluid, andheat it so that it outputs vapor phase working fluid that thereafter bedirected to the target space to heat it.

In another embodiment, the air conditioning system is configured suchthat the vapor phase working fluid that is output by the hot thermalenergy storage unit and thereafter directed to the target space,transmits heat to the target space and thereby condenses.

In yet another embodiment, the condensing unit is configured to beoperable only on received vapor phase working fluid that is within adistinct pressure range, and the suction gas pressurizer and distributorensemble is configured to output vapor phase working fluid that iswithin the distinct pressure range.

In still another embodiment, the cold thermal energy storage unitincludes a phase change material within a circuit that interfaces withthe piping via a heat exchanger.

In a further embodiment, an air conditioning system further includes: asecond condensing unit; a second liquid pressurizer and distributorensemble; a second target space; and a condenser; where: the condensingunit and the second condensing unit are operatively connected by pipingto the condenser; and the second condensing unit, the second liquidpressurizer and distributor ensemble, the second target space, and thecold thermal energy storage unit are operatively connected by pipingsuch that vapor compression cycles can be simultaneously implementedthat result in the cooling of the cold thermal energy storage unit andthe target space.

BRIEF DESCRIPTION OF THE DRAWINGS

FIGS. 1A-1E illustrate a robust air conditioning system in accordancewith certain embodiments of the invention.

FIGS. 2A-2I illustrate a robust air conditioning system operable toprovide heating to a targeted space in accordance with certainembodiments of the invention.

FIGS. 3A-3K illustrate a robust air conditioning system including adistinct hot thermal storage unit to further facilitate the heating of atargeted space in accordance with certain embodiments of the invention.

FIGS. 4A-4E illustrate a configuration for and operation of a condensingunit of robust air conditioning systems in accordance with certainembodiments of the invention.

FIG. 5 illustrates a configuration for a condensing unit of robust airconditioning systems incorporating cold thermal energy storage devicesoperable to provide cooling and/or heating services in accordance withcertain embodiments of the invention.

FIGS. 6A-6C illustrate a configuration for and operation of a condensingunit with a secondary heat transfer loop and integrated heat source ofrobust air conditioning systems incorporating cold thermal energystorage devices operable to provide cooling and/or heating services inaccordance with certain embodiments of the invention.

FIG. 7 illustrates a configuration for a condensing unit employing asuction line heat exchanger of robust air conditioning systemsincorporating cold thermal energy storage devices in accordance withcertain embodiments of the invention.

FIG. 8 depicts a configuration for a target space accepting coolingservices of robust air conditioning systems incorporating cold thermalenergy storage devices in accordance with certain embodiments of theinvention.

FIG. 9 illustrates a configuration of target space accepting heat andcooling services of robust air conditioning systems incorporating coldthermal energy storage devices in accordance with certain embodiments ofthe invention.

FIG. 10 illustrates a target space utilizing a branch selectors andterminal units of robust air conditioning systems incorporating coldthermal energy storage devices in accordance with certain embodiments ofthe invention.

FIG. 11. Illustrates a configuration for a liquid pressurizer anddistributor ensemble of robust air conditioning systems incorporatingcold thermal energy storage devices in accordance with certainembodiments of the invention.

FIGS. 12A-12C illustrate a cold thermal store of robust air conditioningsystems incorporating cold thermal energy storage devices in accordancewith certain embodiments of the invention.

FIGS. 13A-13C illustrate a cold thermal store employing two stageexpansion of robust air conditioning systems incorporating cold thermalenergy storage devices in accordance with certain embodiments of theinvention.

FIGS. 14A-14C illustrate a cold thermal store employing two stageexpansion and a secondary heat transfer fluid store of robust airconditioning systems incorporating cold thermal energy storage devicesin accordance with certain embodiments of the invention.

FIGS. 15A-15C illustrate a configuration for and operation of a coldthermal store employing a cascade vapor compression cycle of robust airconditioning systems incorporating cold thermal energy storage devicesin accordance with certain embodiments of the invention.

FIGS. 16A-16C illustrate a configuration for and operation of a coldthermal store employing a cascade vapor compression cycle and asecondary heat transfer loop of robust air conditioning systemsincorporating cold thermal energy storage devices in accordance withcertain embodiments of the invention.

FIGS. 17A-17C illustrate a configuration for and operation of a coldthermal store employing a stand-alone charging vapor compression cycleand a secondary heat transfer loop of robust air conditioning systemsincorporating cold thermal energy storage devices in accordance withcertain embodiments of the invention.

FIG. 18 illustrates a configuration of a suction gasequalizer/distributor in accordance with certain embodiments of theinvention.

FIG. 19 illustrates an additional configuration of a suction gasequalizer/distributor in accordance with certain embodiments of theinvention.

FIG. 20 illustrates a configuration of a hot thermal store of robust airconditioning systems incorporating cold and hot thermal energy storagedevices units in accordance with certain embodiments of the invention.

FIG. 21 illustrates a configuration of a heat source of robust airconditioning systems incorporating cold and hot thermal energy storagedevices in accordance with certain embodiments of the invention.

FIGS. 22A-22C illustrate a multiple connected configuration for andoperation of robust air conditioning systems incorporating both hot acold thermal energy storage units in accordance with certain embodimentsof the invention.

FIGS. 23A-23C illustrate a multiple connected configuration for andoperation of robust air conditioning systems incorporating cold thermalenergy storage devices operable to provide cooling and/or heatingservices in accordance with certain embodiments of the invention.

DETAILED DESCRIPTION

Turning now to the drawings, systems and methods for implementing robustair conditioning systems that are operable such that an included coldthermal energy storage unit can be cooled to a temperature lower thanthe temperature desired for a target space while the target space issimultaneously cooled to the desired temperature, such that thetemperature desired for the target space can subsequently be establishedand/or maintained by the cold thermal energy storage unit irrespectiveof whether the cold thermal energy storage unit is being principallyrelied on to cool the target space or whether an included poweredcondensing unit is being relied on to cool the target space. In a numberof embodiments, an air conditioning system is configured to cool theincluded cold thermal energy storage unit to a temperature lower thanthat desired for the target space such that—when the cold thermal energystorage unit is principally relied on to establish/maintain the desiredtemperature for the target space—the associated working fluid can beiteratively circulated through the target space and the cold thermalenergy storage unit such that: (1) as the working fluid passes throughthe target space it substantially evaporates and absorbs heat within thetarget space so that the desired temperature for the target space can beestablished/maintained, and (2) when the substantially evaporatedworking fluid passes through the cold thermal energy storage unit, thelow temperature of the cold thermal energy storage unit is sufficient tocause the condensation of the substantially vapor phase working fluid,e.g. so that it can be reintroduced to the target space and continue toremove heat. In this way, the target space can be held at a precisedesired temperature irrespective of whether the air conditioning systemis principally relying on the cold thermal energy storage unit toprovide cooling or whether the air conditioning system is relying on apowered condensing unit (e.g. continually powered by a connection to apower grid) to provide cooling.

As can be appreciated, the continual removal of heat from a targetedspace (e.g. as happens in refrigeration) can be a substantially energyintensive operation. Moreover, given the reliance by modern society onthe creation of comfortable living environments and refrigeration(especially refrigerated warehouses and grocery stores), it can furtherbe appreciated how such systems can impose a substantial burden on powergeneration facilities. To mitigate these potential burdens on powerinfrastructure, many electricity providers impose a time-of-use (TOU)pricing schedule—e.g. charging more for providing electricity during theday where the demand for electricity/cooling is typically greater—so asto address load balancing/intermittency problems on the grid.Consequently, to take advantage of the tiered pricing, many electricityconsumers (e.g. grocers and warehouse operators) have focused ondeveloping/implementing energy storage technologies enabling them topurchase energy at a lower rate (e.g. during middle of the night), andstore it for use during the day (when the cost of electricity ishigher). As can be appreciated, this energy storage behind-the-meter canprovide a substantial economic benefit for such TOU customers. Note thatthis economic benefit is accentuated when the consumer has a very smallload factor defined as the average load divided by maximum load in agiven time period.

Thermal energy storage (TES) refers to accruing thermal energy, andstoring it for later use, and is often implemented in the context of airconditioning systems. For example, in some instances, flake and slushyice is regularly generated to maintain the temperature of productsduring transport or display; such methods surround the products such aspoultry and fish directly with a phase change material (PCM) such as iceor brine. In U.S. Pat. No. 4,280,335, a method for utilizing an ice bankPCM to provide cooling load for cooled display cases and the ‘heatingventilating, and air conditioning’ (“HVAC”) system of a supermarket isenumerated. In this method, coolant in the form of liquid water isproduced from the ice bank and is pumped to display cases and the HVACsystem to offset energy consumption. The disclosure of U.S. Pat. No.4,280,335 is incorporated by reference herein. Other notable prior artincludes U.S. Pat. No. 5,383,339, which presents an apparatus thatcouples to an existing refrigeration system to cool a PCM. This PCM TESis then utilized to offset electricity demand by subcooling the liquidrefrigerant of a second auxiliary refrigeration circuit in order toincrease its cooling capacity and improve the refrigeration system'sefficiency during discharge mode. The disclosure of U.S. Pat. No.5,383,339 is incorporated by reference herein.

Although previous methods for storing thermal energy within the contextof air conditioning systems have been effective to some extent, thecurrent state of the art can benefit from more robust and effectivemethods for storing and using stored thermal energy. For example, manyprior art air conditioning systems that rely on the implementation of avapor-compression cycle and incorporate thermal energy storagemechanisms are not configured such that the associated thermal energystorage unit can be principally relied on to provide cooling to the sameextent as when the air conditioning system utilizes a poweredcondenser/compressor (e.g. powered by the grid). Rather, many suchsystems utilize an included thermal energy storage unit as asupplemental mechanism to facilitate cooling; e.g. in many such systems,separate compressor and condenser units are still relied on toeffectuate the vapor-compression cycle. Alternatively, in a number ofsuch systems, the included thermal energy storage unit can beprincipally relied on to provide for cooling, but not to the same extentas when the air conditioning system utilizes condenser/compressor units.Although not as robust, such systems may find use where precise coolingtemperatures are not required—e.g. the cooling of a living quarters. Bycontrast, such systems may not be sufficient in situations such asrefrigeration, where precise cooling temperatures are desired.

Against this backdrop, many embodiments of the invention implementrobust air conditioning systems whereby a cold thermal energy storageunit is included within a cooling circuit, where the air conditioningsystem is configured such that a desired temperature for a target spacecan be maintained irrespective of whether the cold thermal energystorage unit is being principally relied on to cool the target space orwhether the air conditioning system is relying on a separately poweredcondensing unit (e.g. including a compressor unit and a condenser unit)to help cool the target space. For example, in a number of embodiments,an air conditioning system incorporates a cold thermal energy storagedevice that is configured to be cooled to a temperature lower than thatdesired for a targeted space. For instance, the air conditioning systemcan utilize an incorporated powered condensing unit to cool the coldthermal energy storage unit to a temperature lower than that desired fora targeted space; note that the air conditioning system can beconfigured such that it can simultaneously utilize the poweredcondensing unit to establish/maintain the desired temperature for thetargeted space. The air conditioning system can further be configuredsuch that the thermal energy stored in the cold thermal energy storageunit (which was cooled to a temperature lower than that desired for thetarget space) can thereafter be principally relied on (e.g.substantially without the assistance of a powered condensing unit) toestablish/maintain the desired temperature for the targeted space for atleast some period of time. In many embodiments, the air conditioningsystem is configured such that the cold thermal energy storage unit canbe cooled to a temperature lower than that desired for the target spacesuch that—when the cold thermal energy storage unit is principallyrelied on to cool the target space—the associated working fluid isiteratively circulated through the target space and the cold thermalenergy storage unit such that: (1) as the working fluid passes throughthe target space it evaporates and absorbs heat within the target spaceso that the desired temperature for the target space can beestablished/maintained, and (2) when the working fluid passes throughthe cold thermal energy storage unit, the low temperature of the coldthermal energy storage unit is sufficient to cause the condensation ofthe vapor phase working fluid, e.g. so that it can be reintroduced tothe target space to continue to absorb heat. In a number of embodiments,these configurations can allow for any included compressors orcondensers to be deactivated when the thermal energy storage unit isbeing principally relied on to provide cooling; in other words, thetarget space can be cooled to the desired temperature even in theabsence of the operation of condensers and compressors. As can beappreciated, the operation of the compressors and condensers is theprincipal source of energy consumption for many air conditioningsystems.

In general, such robust air conditioning systems can provide forsubstantial energy efficiency and financial savings. Moreover, suchsystems can further be utilized for their inherent ability to provideeffective backup refrigeration services, e.g. in the case of a powerdisruption. Configurations for robust air conditioning systems, alongwith their respective operation, in accordance with many embodiments ofthe invention are now discussed below.

Configurations for and The Operation of Robust Air Conditioning SystemsIncorporating Cold Thermal Energy Storage Devices

In many embodiments, robust air conditioning systems incorporate a coldthermal energy storage unit within a cooling circuit such that a desiredtemperature for a target space can be established/maintainedirrespective of whether an included condensing unit is being relied onto provide the cooling service or whether an included cold thermalenergy storage unit is being relied on—e.g. without the assistance ofthe powered condensing unit—to provide the cooling service. In numerousembodiments, robust air conditioning systems are configured to beoperable to establish and/or maintain a temperature for the includedcold thermal energy storage unit that is lower than the temperaturedesired for the target space, while simultaneously cooling the targetspace to the desired temperature. In this way, the thermal energystorage unit can thereafter be principally relied on—e.g. without theassistance of a powered condensing unit—to cool the target space to thesame extent that the included, powered, condensing unit can. Note that,as can be appreciated, the air conditioning system may still requirepower for operation of ancillary components.

In many embodiments air conditioning systems are configured to implementvapor-compression cycles to cool a target space to a desired temperatureas well as to cool a cold thermal energy storage unit to a temperaturelower than the temperature desired for the target space. For example,FIGS. 1A-1E illustrate the configuration and operation of a robust airconditioning system that is operable to cool an included cold thermalenergy storage unit using a vapor compression cycle to a greater extentthan a target space, while simultaneously cooling the target space, inaccordance with an embodiment of the invention. Note that throughout allof the figures depicted in the instant application, valves may not beexplicitly depicted. However, as can be appreciated, valves can beimplemented any of the depicted figures to facilitate the desired flow.In any case, FIG. 1A illustrates the configuration of the robust airconditioning system; more specifically, FIG. 1A illustrates that arobust air conditioning system 100 includes a condensing unit 102, atarget space 104, a liquid pressurizer and distributor ensemble 106, acold thermal energy storage unit 108, and a suction gas pressurizer anddistributor ensemble 110, all of which are operatively interconnected bypiping such that a vapor-compression cycle can be implemented to coolthe target space 104 using either the condensing unit 102 or the coldthermal energy storage unit 108, and further configured such that aworking fluid can be circulated through the cold energy storage unit 108and the target space 104 to transport heat as desired. Importantly,within the context of this application, the suction gas pressurizer anddistributor ensemble is sometimes referred to as the ‘suctiongas/equalizer ensemble’ or ‘suction gas/equalizer,’ or ‘suction gasequalizer/distributor ensemble’, or ‘suction gas equalizer/distributor,’or the like. Additionally, within the context of the application, as canbe appreciated, references to e.g. low temperature/pressure and hightemperature pressure are relative, and can be understood to beinterpreted within the context of a vapor compression cycle.

The condensing unit 102 is generally operable to pressurize and/orcondense received low pressure, low temperature vapor phase workingfluid (e.g. exiting from the target space 104 and/or the thermal energystorage unit 108) such that it changes phase to a high temperature, highpressure liquid, e.g. within the context of a vapor-compression cycle.Although the condensing unit 102 is depicted schematically, it should beappreciated that it can be implemented using any of variety of schemes.For example, in many embodiments, the condensing unit comprises acompressor—to compress received vapor phase working fluid—and acondenser to condense the high pressure vapor phase working fluid to aliquid phase working fluid. Of course, to be clear, a condensing unitcan be effectuated in any of a variety of ways in accordance withembodiments of the invention. Examples of some of the condensing unitsthat can be implemented in the depicted figures are discussed insubsequent sections below.

The liquid pressurizer and distributor ensemble 106 generally operatesto pressurize and/or circulate working fluid as desired to facilitatethe operation of the air conditioning system 100 in accordance with anyof its various operating modes. For example, the liquid pressurizer anddistributor ensemble 106 can circulate working fluid through the coldthermal energy storage unit 108, through the target space, orsimultaneously through each of the cold thermal energy storage unit 108and the target space 104. In general, the liquid pressurizer anddistributor ensemble 106 functions to accept liquid phase flow from anyconnected components, alter the flow pressure as necessary (ifappropriate), and/or distribute the received flow to an appropriateconnected component in accordance with any of the air conditioningsystem's operating modes. Additionally, note that the liquid pressurizerand distributor ensemble 106 can be implemented using any of a varietyof components. For example, any suitable pump can be used to pressurizereceived liquid phase working fluid, and any suitable control apparatuscan be implemented to redirect the working fluid as desired. To beclear, embodiments of the invention are not limited to theimplementation of particular configurations for liquid pressurizer anddistributor ensembles. Examples of some of the liquid pressurizer anddistributor ensembles that can be incorporated are discussed insubsequent sections below. Importantly, within the context of theinstant application, the term ‘liquid pressurizer and distributorensemble’ can reference even those devices that are only operable tocontrollably distribute liquid phase working fluid. Additionally, withinthe context of this application, the liquid pressurizer and distributorensemble is sometimes referred to as the ‘liquid pressurizer/distributorensemble’ or ‘liquid pressurizer/distributor,’ or the like.

The target space 104 includes the target of the cooling efforts. As canbe appreciated, in many embodiments, the target space further includesan expansion device operable to reduce the pressure and temperature of areceived working fluid (e.g. such that a vapor-compression cycle can beimplemented). Although the target space 104 is depicted schematically,it should be appreciated that any suitable target space can beimplemented in accordance with many embodiments of the invention. Forexample, in many embodiments, the target space is a living quarters. Ina number of embodiments, the target space 104 is an evaporator (e.g. inthe context of refrigeration). Additionally, while FIG. 1A schematicallydepicts a single contiguous volume that is a target space, in manyembodiments, the target space includes a plurality of discrete volumes;corresponding piping can be implemented such that working fluid cancirculate through each of the plurality of volumes within the targetspace. In any case, it should be clear that any suitable space can bethe target of cooling efforts in accordance with embodiments of theinvention.

The suction gas pressurizer and distributor ensemble 110 generallyoperates to prepare and/or distribute received vapor phase working fluidfor further treatment, e.g. for sending to the condensing unit 102 orsending to the cold thermal energy storage unit 108. In a number ofembodiments, the suction gas/equalizer ensemble 110 is configured topressurize (or depressurize) received vapor phase working fluid so thatit is suitable to be received by further respective treatment modules.For example, in some embodiments, the condensing unit 102 requiresreceipt of vapor phase working fluid within a specified pressure range.Similarly, in a number of embodiments, the cold thermal energy storageunit 108 requires receipt of vapor phase working fluid within aspecified pressure range. Moreover, as with the liquid pressurizer anddistributor ensemble 106, the suction gas/equalizer ensemble 110 can beimplemented using any of a variety of components. For example, any of anumber of pressure regulating mechanisms (e.g. compressors and pressureregulators) can be incorporated with any of a variety of fluid controlmechanisms to implement the suction gas/equalizer ensemble 110. Examplesof some of the suction gas/equalizer ensembles are discussed insubsequent sections below.

The cold thermal energy storage unit 108 generally operates to storethermal energy for subsequent utilization. For instance, as can beappreciated, the cold thermal energy storage unit can be cooled to a lowtemperature, and can operate to retain the cold temperature for extendedperiods of time (e.g. substantially without assistance). For example,thermal energy can be stored within the cold thermal energy storage unit108 at a time when electricity rates are low, and then used to cool thetarget space 104 at a time when electricity rates are high, therebymitigating the use of the condensing unit 102. Any suitable cold thermalenergy storage unit 108 can be implemented in accordance with manyembodiments of the invention. For example, in many embodiments, a phasechange material encased in thermal insulation is implemented toeffectuate the cold thermal energy storage unit 108. Additionally, asalluded to above, in many embodiments, the air conditioning system 100is configured to be operable to establish a temperature for the coldthermal energy storage unit 108 that is lower than that desired for thetarget space 104. This can be achieved in any of a variety of ways. Forexample, the cold thermal energy storage unit 108 includes an expansionvalve configured to reduce the pressure and temperature of receivedworking fluid to a greater extent than any expansion valves incorporatedwithin the target space 104. Examples of some cold thermal energystorage units that can be incorporated in accordance with embodiments ofthe invention are discussed below.

Importantly, as can be appreciated by one of ordinary skill in the artand as discussed above, although the configuration depicted in FIG. 1Adoes not specifically illustrate valves, valves can of course beimplemented to control the circulation of working fluid through the airconditioning system. Indeed, any of a variety of supplementarycomponents can be incorporated to facilitate the operation of the airconditioning system 100 in accordance with many embodiments of theinvention. For example, as can be appreciated, in many embodiments,liquid gas separators are incorporated within the system to increaseoperational efficiency of the implemented vapor-compression cycles. Tobe clear though, any of a variety of supplementary components can beincorporated in accordance with many embodiments of the invention.

FIG. 1B illustrates how the air conditioning system 100 can operate toestablish/maintain a desired temperature for the targeted space 104principally using the condensing unit 102. In particular, the boldedlines (and arrows) depict the circulation of a working fluid so as toimplement a vapor-compression cycle that can cool the target space 104using the condensing unit 102. More specifically, in the illustratedembodiment, the condensing unit 102 acts to condense incoming vaporphase working fluid that is low pressure, low temperature to a(relatively) high temperature, high pressure liquid phase. As mentionedabove, the condensing unit 102 can be implemented via any suitablemechanism(s) in accordance with many embodiments of the invention. Thehigh temperature liquid phase working fluid is then sent to the liquidpressure and distributor ensemble 106 where it is pressurized, ifnecessary, and directed to the target space 104. At the target space104, the working fluid is made to expand so that it experiences apressure drop and a correlated temperature drop; in this way, the lowpressure, low temperature saturated fluid can continue its circulationthrough the target space 104 and absorb heat from the target space 104.Consequently, the working fluid is made to evaporate. As mentionedabove, the target space 104 can be any suitable space in accordance withcertain embodiments of the invention, including but not limited to aliving quarters or an evaporator. The low pressure, low temperaturevapor phase working fluid is subsequently redirected to the suctiongas/equalizer ensemble 110, where it is pressurized—if necessary—andredirected for re-entry into the condensing unit 102, e.g. so that thevapor-compression cycle can continue. Accordingly, it is seen how therobust air conditioning system 100 can implement a vapor-compressioncycle using a condensing unit 102 as the engine for cooling the targetspace 104. Needless to say any suitable working fluid can beimplemented. For example, any of a variety of refrigerants can beincorporated.

FIG. 1C illustrates how the robust air conditioning system 100 canoperate to store thermal energy. In particular, it is illustrated how avapor-compression cycle can be implemented using the condensing unit 102to store thermal energy within the cold thermal energy storage unit 108.More specifically, it is depicted that the condensing unit 102 causesthe condensation of a circulated working fluid, which is then redirectedby the liquid pressurizer and distributor ensemble 106 to the coldthermal energy storage unit 108. Importantly, the air conditioningsystem 100 is configured such that the vapor-compression cycle cools thecold thermal energy storage unit 108 to a greater extent compared to thetarget space. In other words, the temperature of the cold thermal energystore can be set to a temperature lower than that desired for the targetspace 104. As alluded to above, this can be achieved in any of a varietyof ways. For example in many embodiments, the cold thermal energystorage unit 108 includes an expansion valve that decreases the pressureand temperature of a received working fluid to a greater extent than anyexpansion valve incorporated within the target space 104. In this way,thermal energy can be stored sufficient to effectivelyestablish/maintain the desired temperature for the target space 104.

While FIG. 1C illustrates the storing of thermal energy by using thecondensing unit 102 to implement a vapor-compression cycle, FIG. 1Dillustrates how the robust air conditioning system 100 can operate tosimultaneously cool the target space 104 and store thermal energy usingthe condensing unit. As can be appreciated, in the illustratedembodiment, vapor-compression cycles are implemented in a manner similarto those seen in and described with respect to FIGS. 1B and 1C. It isdepicted how the liquid pressurizer and distributor ensemble 106 and thesuction gas/equalizer 110 control the division and aggregation of theflow of the working fluid. For example, it is depicted that the liquidpressurizer and distributor ensemble splits the liquid phase workingfluid, so that part of the flow is directed to the cold thermal energystorage unit 108 and part of the flow is directed to the target space104. In this way, both the target space 104 and the cold thermal energystorage unit 104 can be cooled. The illustrated embodiment furtherdepicts that the suction gas/equalizer 110 can operate to equalize vaporpressure working fluid received from both the target space 104 and thethermal energy storage unit 108, and additionally implement any furthertreating processes, prior to sending it to the condensing unit 102.

FIG. 1 E illustrates how the robust air conditioning system 100 canoperate to cool the target space 104 using stored thermal energy in thethermal energy storage unit 108. In general, fluid can be circulatedthrough the cold thermal energy storage unit 108 and the target space104. As the cold thermal energy storage unit 108 is set at a temperaturelower than that desired for the target space 104, the circulation of thefluid will facilitate the transport of heat away from the target space104 and toward the cold thermal energy storage 108, and importantly, thetarget space can be held at the same temperature as if it were poweredby the condensing unit 102. More specifically, the illustratedembodiment depicts that fluid is circulated through the cold thermalenergy storage unit 108, the liquid pressurizer and distributor ensemble106, the target space 104, and the suction gas/equalizer 110. As can beappreciated and as illustrated, the piping can be implemented such thatit allows for fluid flow in either direction. In a number ofembodiments, the air conditioning system 100 is configured such that thefluid flow is made to condense by the cold thermal energy storage unit108 and evaporate by the target space 104. This can be achieved byconfiguring the air conditioning system 100 such that it is operable toestablish a temperature for the cold thermal energy storage unit 108that is sufficiently lower than that desired for the target space 104.Importantly, it is depicted that the illustrated operating mode does notrequire the operation of the condensing unit 102, which typically drawsmuch power.

Notably, because the depicted system 100 is operable to simultaneouslyestablish/maintain specified temperatures for each of the cold thermalenergy storage 108 unit and the target space 104, the air conditioningsystem 100 is capable of continuously establishing/maintaining a desiredtemperature for the target space. For example, where the airconditioning system 100 is used as a refrigerator, the air conditioningsystem 100 can operate to cool the target space 104 and the cold thermalenergy storage unit 108 using the condensing unit 102 during the night(when the cost of electricity is cheaper), and then use the cold thermalenergy storage unit 108 to cool the target space 104 during the day(when the cost of electricity is more expensive).

Although the above-discussion has principally regarded robust airconditioning systems incorporating cold thermal energy storage units andconfigured to cool a target space, in many embodiments, air conditioningsystems are further configured to be operable to heat a target spaceusing an integrated heating source. Air conditioning systems that arefurther configured to be operable to heat a target space are nowdiscussed below.

Configurations for and the Operation of Robust Air Conditioning SystemsIncorporating Cold Thermal Energy Storage Devices and Operable toProvide Cooling and/or Heating Services

In many embodiments, robust air conditioning systems incorporateintegrated heating mechanisms such that they are operable to effectivelyand efficiently provide heating and/or cooling services. Any of avariety of heating mechanisms can be incorporated to heat the targetspace in accordance with many embodiments of the invention. For example,in many embodiments, condensing units are implemented that are operableto output heated vapor phase working fluid (e.g. by using a compressor),which can then be circulated to provide heating for a target space. In anumber of embodiments, the condensing unit includes a distinctintegrated heating mechanism, capable of heating the target space. Inmany embodiments, the heating mechanism does not require access to apower grid to operate. For example, in a number of embodiments, a gasheater is integrated into the air conditioning system and used toprovide heating functionality. In this way, the air conditioning systemcan provide heating and cooling services without having to principallyrely on a power grid. To be clear, any of a variety of heatingmechanisms can be integrated into robust air conditioning systems inaccordance with embodiments of the invention. For example, as alluded toabove, condensing units that are operable to use an integratedcompressor to compress an incoming vapor phase working fluid and therebygenerate a heated vapor phase working fluid can be integrated into anair conditioning system.

FIGS. 2A-2I illustrate a configuration for and the operation of a robustair conditioning system that includes an integrated heat source, as wellas various modes of operation. In particular, FIG. 2A illustrates therobust air conditioning system including an integrated heat sourcewithin the condensing unit. More specifically, the structure of the airconditioning system 200 is similar to that seen with respect to FIG. 1A,insofar as it includes: a condensing unit 202, a target space 204, aliquid pressurizer and distributor ensemble 206, a cold thermal energystorage unit 208, and a suction gas/equalizer ensemble 210. The airconditioning system further includes a separate pipeline 213 that canchannel heat, in the form of vapor phase working fluid, from thecondensing unit 202 to the target space 204. In the illustratedembodiment, an integrated heating source 211 is assimilated within thecondensing unit 202. As stated above, any of a variety of heatingsources can be integrated. In many embodiments, the heating source isgas powered and therefore does not require access to a power grid inorder to operate. In this way, the air conditioning system 200 canprovide heating and/or cooling services (via thermal energy stored inthe cold thermal energy storage unit 208) without principally relying onaccess to a power grid.

FIG. 2B illustrates the operation of the air conditioning system 200depicted in FIG. 2A to cool and/or heat the target space 204. Forexample, in some instances it may be desired that a certain portion ofthe target space 204 be heated, while another portion be cooled. Forinstance, on many occasions it is desirable to prevent the buildup offrost within a freezer; accordingly, heat can be directed to those areasthat are prone to frost development, while the other portions are keptcool. In other instances, in the context of air conditioning livingquarters, it may be desirable to cool one floor of a building, but heatanother floor of a building (e.g. a basement). In any case, theillustration is similar to that seen with respect to FIG. 1B insofar asit depicts the implementation of a vapor-compression cycle by thecondensing unit 202 to cool the target space 204. In the illustratedembodiment, it is further depicted that, alternatively orsimultaneously, the integrated heating source 211 can be used to heatand boil the working fluid such that it can be circulated via thededicated pipeline 213 to those aspects of the target space 204 desiringheat. In the illustrated embodiment, it is depicted that the heatedvapor phase working fluid condenses after rejecting the heat to thetarget space 204. Consequently, the condensed fluid can be recirculatedthrough the condensing unit via the liquid pressurizer and distributorensemble 206. In particular, it is depicted that target space 204 causesthe condensation of the heated vapor phase working fluid, e.g. so thatit is suitable to be controlled by the liquid pressurizer anddistributor ensemble 206. In the illustrated embodiment, it is depictedthat the pipelines running to and from the liquid pressurizer anddistributor ensemble 206 are operable to allow for the flow of workingfluid each way. As can be appreciated, when both heating and coolingcycles are implemented, the overall direction of the flow will beprincipally based on the extent of cooling being desired relative to theextent of heating being desired.

FIG. 2C illustrates the operation of the air conditioning system 200store thermal energy within the cold thermal storage unit 208. As can beappreciated, the operation is similar to that seen in FIG. 1C insofar asit illustrates the implementation of a vapor-compression cycle to coolthe cold thermal energy storage unit 208 to any desired temperature.

FIG. 2D illustrates the operation of the air conditioning system 200depicted in FIG. 2A to charge the cold thermal storage unit 208, as wellas provide heating for the target space 204. As can be appreciated, theillustration is similar to that seen in FIG. 2C insofar as it depictsthe implementation of a vapor-compression cycle to cool the cold thermalenergy storage unit 208 to a desired temperature. However, FIG. 2D alsodepicts the circulation of a heated fluid to heat the target space.Similar to before, when the heated vapor phase working fluid condenses,it can leverage the liquid pressurizer and distributor ensemble 206 tofacilitate its circulation. Note that the associated pipelines areadapted for flow in both directions, such that it can return condensedliquid after it has heated the target space 204 and/or can delivercondensed liquid from the condensing unit 202 to the cold thermalstorage unit 208.

FIG. 2E illustrates the operation of the air conditioning system 200 tostore thermal energy in the cold thermal energy storage unit 208 as wellas provide cooling for the target space 204. As can be appreciated, theoperation of the air conditioning system 200 in this respect is similarto that seen in FIG. 1E.

FIG. 2F illustrates the operation of the air conditioning system 200depicted in FIG. 2A to store thermal energy in the cold thermal energystorage unit 208, to cool the target space 204, as well as to provideheat to the target space 204. As can be appreciated, the illustration issimilar to that seen with respect to FIG. 2E, except that theillustration further depicts that a heated fluid is circulated throughthe target heated space. The illustration depicts that the liquidpressurizer and distributor ensemble 206 can control the liquid phaseworking fluid fluid circulation for each of the vapor-compression cycles(e.g. the vapor-compression cycle configured to cool the cold thermalenergy storage unit 208 and the target space 204) as well as thecirculation of the fluid used to heat the target space.

FIG. 2G illustrates the operation of the air conditioning system 200 toheat the target space 204. In particular, it is illustrated that theheating fluid (e.g. the boiled working fluid) is circulated through theintegrated heat source 212 within the condensing unit 202, the targetspace 204, and the liquid pressurizer and distributor ensemble 206.Accordingly, the fluid can deliver heat generated by the integrated heatsource 212 to the target space 208.

FIG. 2H illustrates the operation of the air conditioning system 200 tocool the target space 204 to the desired temperature using the coldthermal energy storage unit 208. As can be appreciated, the operation issimilar to that depicted in FIG. 1E.

FIG. 2I illustrates the operation of the air conditioning system 200depicted in FIG. 2A to cool the target space 204 using the cold thermalenergy storage unit 208 as well as to deliver heat to the target space204 using heat generated by the integrated heating source 211. As can beappreciated, the illustration is similar to that seen in FIG. 2H insofaras it depicts the circulation of a working fluid between the coldthermal energy storage unit 208 and the target space 204, except that itfurther depicts that a heated fluid is circulated through the condensingunit 202 and the target space 204. This mode of operation can beeffectuated largely without access to a power grid (given that theintegrated heating source can largely operate without access to a powergrid). In general, as can be appreciated, the above describedconfigurations offer a robust air conditioning solution that cancontinuously provide air conditioning services (both heating andcooling), even without principal reliance on a power grid.

While the above discussion has largely focused on robust airconditioning systems including an integrated heat source within aconstituent condensing unit, it should be appreciated that integratedheat sources can be assimilated in any of a variety of ways inaccordance with embodiments of the invention. In many embodiments,integrated heat sources can be incorporated within a robust airconditioning system outside of the constituent condensing unit. In anumber of embodiments, the integrated heat source is associated with anentirely distinct circulation piping—e.g. without any overlap withpiping used to implement a vapor-compression cycle. In severalembodiments, the integrated heat source is not associated with the sameliquid pressurizer and distributor ensemble that is used to facilitatethe implementation of a vapor-compressor cycle; rather it is in fluidcommunication with a separate fluid circulation pump. As can beappreciated, the above-described configurations can be implemented inany of a variety of configurations in accordance with many embodimentsof the invention.

Additionally, while the above embodiments have principally regarded theintegration of a heat source within an air conditioning system, in anumber of embodiments, a separate hot thermal energy storage unit isadditionally incorporated within a robust air conditioning system, suchthat the air conditioning system can provide both heating and coolingfunctionalities via thermal energy storage units. Air conditioningsystems incorporating heated thermal energy storage units are nowdiscussed below in greater detail.

Configurations for and the Operation of Robust Air Conditioning SystemsIncorporating Both Hot and Cold Thermal Energy Storage Units

In many embodiments, a robust air conditioning system includes distincthot and cold thermal energy storage units, and is operable to use themto heat and/or cool, a targeted space. For example, in many embodiments,a hot thermal energy storage unit is in fluid communication with anintegrated heat source embedded within a condensing unit. The integratedheat source can be either one that is principally powered using accessto the power grid, or one that can operate without access to a powergrid. In many embodiments, the condensing unit itself provides thefunctionality of the integrated heat source. For example, in manyembodiments, the condensing unit can be made to implement an operatingmode whereby it can boil working fluid such that the vapor phase workingfluid can be transmitted to the target space for the purposes ofheating. This operating mode can be achieved, for instance, by using acompressor within the condensing unit to compress low temperature gas tohigh temperature gas. In this way, the condensing unit can be consideredto be include an integrated heat source, insofar as the integratedcompressor can be used to provide heat as desired. In effect, theseconfigurations can operate to store thermal energy within the hot andcold thermal energy units using a powered condensing unit. In this way,a target space can be air conditioned either via the condensing unit, oreither of the hot thermal energy storage unit or the cold thermal energystorage unit as appropriate.

For example, FIGS. 3A-3K depict the operation of a robust airconditioning system that includes separate thermal energy storage unitsfor heating and cooling a target space, in accordance with certainembodiments of the invention. In particular, FIG. 3A illustrates thatthe air conditioning system 300 is similar to that seen in FIG. 1Ainsofar as it includes: a condensing unit 302, a target space 304, aliquid pressurizer and distributor ensemble 306, a cold thermal energystorage unit 308, and a suction gas conditioner/distributor 310. FIG. 3Afurther depicts that the air conditioning system 300 further includes ahot thermal energy storage unit 312, and a discharge gas distributor314. Note that in the illustrated embodiment, the condensing unit 302 isoperable to heat (e.g. boil) working fluid so that the heated fluid canbe used to heat either the hot thermal energy storage unit 312 or thetarget space 304. The condensing unit 302, the discharge gas distributor314, the hot thermal storage unit 312, the target space 304, and theliquid pressurizer and distributor ensemble 306 are operativelyconnected by piping so as to allow for the circulation of a heated fluidthrough the target space 304 to heat it, as well as allow thecirculation of a heated fluid through the hot thermal energy storageunit 312 to store thermal energy. As can be appreciated, the hot thermalenergy storage unit 312 can be implemented in any of a variety of ways.For instance, in many embodiments, the hot thermal energy storage unitincludes a thermal storage medium encased in thermal insulation. Furtherexamples of some hot thermal energy storage units that can beincorporated in accordance with embodiments of the invention arediscussed below.

FIG. 3B depicts the operation of the air conditioning system 300 toprovide both heating and cooling services to the target space 304 usingthe condensing unit 302. In the illustrated embodiment, the condensingunit 302 is powered and is configured to effectuate a vapor-compressioncycle to provide cooling services to the target space 304—e.g. as seenabove with respect to FIG. 1B. Concurrently or alternatively, thecondensing unit 302 is powered to create heated vapor phase workingfluid that can be circulated, e.g. via the discharge gas distributor314, through the target space. The heat transfer that occurs between theheated vapor phase working fluid and the target space 304, typicallyworks to condense the fluid into a liquid, which can then be returned tothe condensing unit via the liquid pressurizer and distributor ensemble306. In particular, it is depicted that in the illustrated embodiment,the liquid pressurizer and distributor ensemble 306 controls the flow ofthe working fluid implementing the vapor-compression cycle as well asthe condensed fluid that was used to heat the target space. In this way,the condensing unit 302 can operate to provide both heating and coolingservices to the target space 304.

FIG. 3C illustrates the operation of the air conditioning system 300 tostore thermal energy in the hot thermal energy storage unit 312 as wellas store thermal energy in the cold thermal energy storage unit 308. Ascan be appreciated, the process is similar to that seen in FIGS. 1C and2C, insofar as a vapor-compression cycle is implemented to cool the coldthermal energy storage unit 308 to a temperature less than that desiredfor a target space 304. However, the illustrated embodiment furtherdepicts that a heated fluid (e.g. compressed vapor phase heating fluid)is generated within the condensing unit and directed to the dischargegas distributor 314, which then redirects the heated gas to the hotthermal energy storage unit, which is configured to be operable toabsorb the heat, and retain it for subsequent use. In the illustration,this mode of operation does not provide any air conditioning for thetarget space 304.

FIG. 3D depicts the heating of the target space 304 in conjunction withthe simultaneous storing of thermal energy within the hot thermal energystorage unit 312. The illustration is similar to that seen above withrespect to FIG. 3C insofar as it depicts the storing of thermal energywithin the hot thermal energy storage unit 312; however, FIG. 3D furtherillustrates that a portion of the heated fluid is used to provideheating for the target space 304. The liquid pressurizer and distributorensemble 306 is used to aggregate the condensed fluid that previouslyserved to heat the target space 304 and the hot thermal energy storageunit 312 to deliver it to the condensing unit for heating and furthercirculation.

FIG. 3E depicts the heating of the target space 304, as well as theimplementation of a cooling vapor compression cycle to store thermalenergy within the cold thermal energy storage unit 308. As can beappreciated, the illustrated operation mode is similar to that seen withrespect to FIG. 3B, except that the condensing unit 302 is used toimplement a vapor compression cycle with respect to the cold thermalenergy storage unit 308 as opposed to the target space 304.

FIG. 3F depicts the inverse scenario where the air conditioning system300 is being operated to store thermal energy in the hot thermal energystorage unit 312 and to cool the target space 304 using the condensingunit 302. As can be appreciated, the illustrated operation mode issimilar to that seen with respect to FIG. 3B, except that the heatedfluid is being circulated through the hot thermal energy storage unit312 as opposed to the target space 304.

FIG. 3G depicts the operation of the air conditioning system 300 tosimultaneously cool the cold thermal energy storage unit 308 as well asthe target space 304. The operation mode is similar to that seen withrespect to FIG. 1D.

FIG. 3H depicts the operation of the air conditioning system 300 toprovide heating/cooling to the target space 304 as well as to storethermal energy within the hot thermal energy storage unit 312 and thecold thermal energy storage unit 308. As can be appreciated, theillustrated operating mode is similar to that seen with respect to FIG.3B, except that portions of the circulated heated fluid and the workingfluid are redirected via the gas discharge distributor 314 and theliquid pressurizer distributor ensemble 306 to the hot thermal energystorage unit 312 and the cold thermal energy storage unit 308,respectively.

FIG. 3I depicts the operation of the air conditioning system 300 to heatthe target space 304 using the hot thermal energy storage unit 312. Inparticular, the figure depicts that the working fluid is circulatedthrough the hot thermal energy storage unit 312, the discharge gasdistributor 314, into the target space 304 and back to the liquidpressurizer and distributor ensemble 306.

FIG. 3J depicts the operation of the air conditioning system 300 to coolthe target space using the cold thermal energy storage unit 308. As canbe appreciated, the operation of the air conditioning system 300 issimilar to that seen above with respect to FIG. 1E.

FIG. 3K depicts the operation of the air conditioning system 300 toprovide both heating and cooling services to the target space 304 usingthe hot and cold thermal energy storage units, 312 and 308,respectively. As can be appreciated, the illustrated mode of operationeffectively superimposes the modes of operation depicted in FIGS. 3I and3J.

Several implementations of various components that can be implemented inrobust air conditioning systems in accordance with embodiments of theinvention are now discussed below.

Condensing Units for Implementation Within Robust Air ConditioingSystems

In many embodiments, condensing units are implemented that are suitableto be incorporated within many of the above described air conditioningsystem configurations.

For example, FIGS. 4A-4E illustrate a configuration for and operation ofa condensing unit of robust air conditioning systems. In operation, acondensing unit of robust air conditioning systems can function in fivedistinct modes of being unused, cooling only, mostly cooling withsupplemental heating, heating with supplemental cooling and heating onlyrepresented by FIG. 4A, 4B, 4C, 4D and 4E respectively.

In particular, FIG. 4A illustrates the configuration of a condensingunit 400 which includes a dual use condenser/evaporator 402, anexpansion valve 404 and a compressor 406, all of which are operativelyinterconnected by piping. The condensing unit 400 generally operates togenerate heating or cooling services in the form of high pressure vaporworking fluid or high pressure liquid working fluid when used as acomponent of a robust air condition system. As is the case with allfigures, although not depicted, valves and other components can beincorporated to facilitate the operation of the condensing unit 400 inaccordance with many embodiments of the invention.

The dual use evaporator/condenser 402 generally operates to exchangeheat between a working fluid and some other media in a manner thateither extracts heat from the media and boils the working fluid orprovides heat to the media and condenses the working fluid. Although thedual use evaporator/condenser 402 is schematically depicted it should beappreciated that it can be implemented using any of a variety ofschemes. For example, in many embodiments, the dual useevaporator/condenser 402 comprise coils of a thermally conductivematerial through which the working fluid passes. In another scheme, thedual use evaporator/condenser 402 consists of a braze plate heatexchanger through which the working and target media are circulated.

The expansion device 404 generally operates to expand a higher pressurefluid to a lower pressure. Although the expansion device 404 is depictedschematically it should be appreciated that it can be implemented usingany of a variety of schemes. For example, in many embodiments, theexpansion device 404 comprises an electronic expansion valve. In anotherscheme, the expansion device 404 comprises a turbine. In any case, itshould be clear that any suitable device can be used as an expansiondevice in accordance with embodiments of the invention.

The compressor 406 generally operates to compress a low pressure gas tohigher pressure. Although the compressor 406 is depicted schematicallyit should be appreciated that it can be implemented using a variety ofschemes. For example, in many embodiments, the compressor 406 comprisesa positive displacement device. In another scheme, the compressor 406comprises a dynamic compressor device such as a jet, centrifugal oraxial compressor.

FIG. 4B illustrates how the condensing unit 400 can operate to providecooling in the form of exiting high pressure liquid working fluid (i.e.to the liquid pressurizer/distributor or the like). In particular, thebolded lines (and arrows) depict the circulation of a working fluid.Incoming low pressure vapor working fluid is pressurized by thecompressor 406 into a hotter high pressure vapor. The vapor then travelsthrough the dual use evaporator/condenser 402 where it rejects its heatand condenses into a high pressure liquid. The resulting liquid thenexits the condensing unit 400.

FIG. 4C illustrates how the condensing unit 400 can operate to providemostly cooling with supplemental heating in the form of exiting highpressure liquid working fluid (i.e. to the liquidpressurizer/distributor or the like) and high pressure vapor phaseworking fluid (i.e. to the discharge gas distributor or the target spaceor the like). In particular, the bolded lines (and arrows) depict thecirculation of a working fluid. Incoming low pressure vapor workingfluid is pressurized by the compressor 406 into a hotter high pressurevapor. Some portion of the vapor phase working fluid leaves thecondensing unit 400 while another portion travels to the dual useevaporator/condenser 402 where it is condensed into liquid beforeexiting.

FIG. 4D illustrates how the condensing unit 400 can operate to provideheating with supplemental cooling in the form of exiting hot vapor phaseworking fluid (i.e to the discharge gas distributor or the target spaceor the like). During this operational mode the condensing unit 400 takesin low pressure vapor phase working fluid as well as high pressureliquid. The bolded lines (and arrows) depict the circulation of aworking fluid. Incoming liquid phase working fluid travels through anexpansion valve 404 and into the dual use evaporator/condenser 402 whereit is evaporated into a low pressure gas. This gas stream then joinsadditional low pressure gas received by the condensing unit 400 (i.e.from a suction gas equalizer/distributor or the like) and is pressurizedby the compressor 406. This hot high pressure vapor phase working fluidthen exits the condensing unit 400.

FIG. 4E illustrates how the condensing unit 400 can operate to provideheating in the form of exiting hot high pressure vapor phase workingfluid (i.e. to the discharge gas/distributor or the like). Inparticular, the bolded lines (and arrows) depict the circulation of aworking fluid. During this operational mode the condensing unit 400takes in high pressure liquid. The bolded lines (and arrows) depict thecirculation of a working fluid. Incoming liquid phase working fluidtravels through an expansion valve 404 and into the dual useevaporator/condenser where it is evaporated into a low pressure gas.This gas stream is then pressurized by the compressor 406 and theresulting hot high pressure vapor phase working fluid then exits thecondensing unit 400.

FIG. 5 illustrates a configuration for a condensing unit with integratedheating of robust air conditioning systems incorporating cold thermalenergy storage devices operable to provide cooling and/or heatingservices. More specifically, the structure of the condensing unit withintegrated heating 500 is similar to that seen with respect to FIG. 4A,insofar as it includes: a dual use condenser/evaporator 502, anexpansion valve 504 and a compressor 506, all of which are operativelyinterconnected by piping. In operation, heating services in the form ofhot vapor phase working fluid can be provide without the use of thecompressor 506. Incoming high pressure liquid passes directly throughthe dual use evaporator/condenser 502 and boils before exiting thecondensing unit with integrated heating 500. Though not depicted, othersuitable components such as receivers, flow control valves, sensors,circulation devices, etc., can be added without departing from the scopeof the condensing unit with integrated heating 500 in accordance withmany embodiments.

FIGS. 6A-6C illustrate a configuration for and operation of a condensingunit with a secondary heat transfer loop and integrated heat source ofrobust air conditioning systems incorporating cold thermal energystorage devices operable to provide cooling and/or heating services.

In particular, FIG. 6A illustrates the configuration of a condensingunit 600. More specifically, the structure of the condensing unit withintegrated heating 600 is similar to that seen with respect to FIG. 4Ainsofar as it includes: a dual use condenser/evaporator 602, anexpansion valve 604 and a compressor 606, all of which are operativelyinterconnected by piping. The condensing unit 600 additionally includesa fluid cooled condenser 610 and heat source 608 connected to the dualuse evaporator/condenser by a secondary heat transfer fluid. Though notdepicted, other suitable components such as receivers, flow controlvalves, sensors, circulation devices, etc. can be added withoutdeparting from the scope of the condensing unit with integrated heating600 in accordance with many embodiments.

FIG. 6B depicts the condensing unit 600 in an integrated heating modewhereby the compressor is not required to run to provide hot highpressure vapor phase working fluid. In operation incoming high pressureliquid passes directly through the dual use evaporator/condenser 602which boils before exiting the condensing unit with integrated heating600. The dual use evaporator/condenser 602 is provided heat by the heatsource 608 which is in thermal communication via a secondary heattransfer fluid.

FIG. 6C depicts the condensing unit 600 in heating and cooling modewhereby incoming low pressure vapor working fluid is pressurized by thecompressor 606 into a hotter high pressure vapor. Some portion of thevapor phase working fluid leaves the condensing unit 600 while anotherportion travels to the dual use evaporator/condenser 602 where it iscondensed into liquid before exiting. The dual use evaporator/condenser602 removes heat from the working fluid by employing a fluid cooledcondenser 610 which is in thermal communication via a secondary heattransfer fluid loop.

FIG. 7 illustrates a configuration for a condensing unit employing asuction line heat exchanger of robust air conditioning systems. Inparticular, FIG. 7 depicts the configuration of a condensing unit 700the structure of which is similar to that seen with respect to FIG. 4Ainsofar as it includes: a dual use condenser/evaporator 702, anexpansion valve 704 and a compressor 706, all of which are operativelyinterconnected by piping. The condensing unit 700 additionally employs asuction line heat exchanger 706. As can be appreciated, although notdepicted, valves or other components can be incorporated to facilitatethe operation of the condensing unit 700 and a condensing unit employinga suction line heat exchanger can be effectuated in any of a variety ofways in accordance with embodiments of the invention.

The suction line heat exchanger 706 generally operates to transfer heatbetween liquid phase working fluid and vapor phase working fluid.Although the suction line heat exchanger 706 is depicted schematicallyit should be appreciated that it can be implemented using any of avariety of schemes. For example, in many embodiments, the suction lineheat exchanger 706 comprises a brazed plate heat exchanger. In anotherscheme, the suction line heat exchanger 706 comprises a spiral heatexchanger. In any case, it should be clear that any suitable heatexchanging device can be used as a suction line heat exchanger inaccordance with embodiments of the invention.

While several examples of condensing units that are suitable forimplementation within many of the above described robust airconditioning systems are described, it can be appreciated that any of avariety of condensing units can be implemented that are suitable forincorporation in a number of the above-described robust air conditioningsystems in accordance with many embodiments of the invention.

Target Spaces for Implementation Within Robust Air Conditioing Systems

In many embodiments, target spaces are implemented that are suitable tobe incorporated within many of the above described air conditioningsystem configurations.

For example, FIG. 8 depicts a configuration for a target space 800 whichincludes enclosures 802, expansion devices 804 and evaporators 806. Inmany embodiments the target space 800 is configured to acceptpressurized liquid (i.e. from a liquid pressurizer/distributor ensembleor the like), expand it to a lower pressure via the expansion devices804 and allow it to absorb heat from within the enclosures 802 via theevaporators 806. The low pressure vapor phase working fluid then exitsthe target space 800 (i.e. to a suction gas equalizer/distributorensemble or the like). As can be appreciated, although not depicted,valves or other components can be incorporated to facilitate theoperation of the target space 800 in accordance with many embodiments ofthe invention. Of course, to be clear, a target space can be effectuatedin any of a variety of ways in accordance with embodiments of theinvention.

The enclosures 802 of the target space 800 provide a designated volumein which thermal services are received. Although the enclosures 802 aredepicted schematically it should be appreciated that they can beimplemented using any of a variety of schemes. For example, in manyembodiments, the enclosures 802 comprise refrigeration display cases. Inanother scheme, the enclosures comprise rooms in office buildings. Inyet another scheme, the enclosures 802 comprise general areas or zoneswhere thermal services are applied.

The expansion devices 804 generally operate to expand a higher pressurefluid to a lower pressure. Although the expansion devices 804 aredepicted schematically it should be appreciated that they can beimplemented using any of a variety of schemes. For example, in manyembodiments, the expansion devices 804 comprise electronic expansionvalves. In another scheme, the expansion devices 804 comprise turbines.In any case, it should be clear that any suitable devices can be used asan expansion devices in accordance with embodiments of the invention.

The evaporators 806 generally operate to exchange heat between a workingfluid and some other media in a manner that extracts heat from the mediaand boils the working fluid. Although the evaporators 806 areschematically depicted it should be appreciated that they can beimplemented using any of a variety of schemes. For example, in manyembodiments, the evaporators 806 comprise coils of a thermallyconductive material through which the working fluid passes. In anotherscheme, the evaporators 806 consist of a braze plate heat exchangersthrough which the working fluid and target media of the enclosures 802are circulated.

FIG. 9 illustrates a configuration of a target space 900 which issimilar to that seen with respect to FIG. 8, insofar as it includes:enclosures 902, expansion valves 904. In addition the target spaceconfiguration 900 includes dual use evaporators/condensers 906. Inoperation the target space configuration 900 is able to provide coolingor heating to the enclosures 902 by either expanding an incoming liquidworking fluid and evaporating it or condensing a higher pressure vaporphase working fluid. During cooling, flow is directed from a main liquidline to a specified dual use evaporators/condenser 906. The low pressuresuction gas is then directed out of the target space 900 (i.e. to asuction gas equalizer/distributor ensemble or the like). During heating,hot vaporized working fluid is directed through the dual useevaporators/condensers 906 where it is condensed into a high pressureliquid and is sent to the shared liquid line. From the shared liquidline, liquid can be directed to another dual use evaporators/condenserto provide cooling or leave the target space (e.g. to the liquidpressurizer/distributor ensemble or the like) to be reheated to providecontinued heating services. As can be appreciated, although notdepicted, valves or other components can be incorporated to facilitatethe operation of the target space 900 in accordance with manyembodiments of the invention. Of course, to be clear, a target space canbe effectuated in any of a variety of ways in accordance withembodiments of the invention.

FIG. 10 illustrates a target space utilizing a branch selectors andterminal units 1000. The target space 1000 consists of a branch selector1002 and terminal units 1004 whereby the branch selector 1002 isconnected to terminal units 1004 by piping. In operation the targetspace 1000 takes in hot pressurized vapor and high pressure liquidworking fluid which is directed to a branch connectors 1002. At thebranch selector, either a liquid phase or gas phase working fluid isdirected to the terminal units 1004 depending on their individualheating or cooling requirements. Either a low pressure vapor or a highpressure liquid working fluid returns from the terminal unit 1004. Inthe case that liquid is returned it may be reused by other terminalunits 1004 connected to the branch selector as needed. As can beappreciated, although not depicted, valves or other components can beincorporated to facilitate the operation of the target space 1000 inaccordance with many embodiments of the invention.

While several examples of target spaces that are suitable forimplementation within many of the above described robust airconditioning systems are described, it can be appreciated that any of avariety of target spaces can be implemented that are suitable forincorporation in a number of the above-described robust air conditioningsystems in accordance with many embodiments of the invention.

Liquid Pressurizer and Distributor Ensembles for Implementation WithinRobust Air Conditioning Systems

In many embodiments, liquid pressurizer and distributor ensembles areimplemented that are suitable to be incorporated within many of theabove described air conditioning system configurations.

FIG. 11 Illustrates a configuration for a liquid pressurizer anddistributor ensemble 1100 which includes pressurizing devices 1102,1104, 1106, and 1108 and a liquid receiver 1110. In many embodiments theliquid pressurizer and distributor ensemble is configured to acceptliquid working fluid from any of its branches, store it temporarily inthe receiver 1110, pressurize the working fluid via any of itspressurizing devices 1102, 1104, 1106 and 1108 to requiredspecifications and distribute it to the appropriate connected robust aircondition system component. In many embodiments, a liquid pressurizerand distributor ensemble requires fewer pressurizing devices and/or noreceiver. Although the liquid pressurizer and distributor ensemble 1100is depicted schematically, it should be clear that a liquid pressurizerand distributor ensemble 1100 can be effectuated in any of a variety ofways in accordance with embodiments of the invention. As can beappreciated, although not depicted, valves or other inline componentscan be incorporated to facilitate the operation of the liquidpressurizer and distributor ensemble 1100 in accordance with manyembodiments of the invention.

The pressurizing devices 1102, 1104, 1106, and 1108 generally operate toadd pressure to an incoming stream of liquid. Although the pressurizingdevices 1102, 1104, 1106, and 1108 are depicted schematically, it shouldbe appreciated that they can be implemented using a variety of schemes.For example, in many embodiments, the pressurizing devices 1102, 1104,1106, and 1108 comprise kinetic pumping devices. In another scheme, thepressurizing devices 1102, 1104, 1106, and 1108 comprise positivedisplacement pumping devices.

The receiver 1110 generally operates to provide a buffer storage volumeto the working fluid circuit as to enable the pressurizing devices 1102,1104, 1106, and 1108 to operate smoothly irrespective of the inletconditions to the liquid pressurizer and distributor ensemble. Althoughthe receiver 1110 is schematically depicted, it should be appreciated itcan be implemented using a variety of schemes. For example, in manyembodiments, the receiver 1110 comprises a pressure vessel. In anotherscheme, the receiver comprises extended piping.

While several examples of liquid pressurizer and distributor ensemblesthat are suitable for implementation within many of the above describedrobust air conditioning systems are described, it can be appreciatedthat any of a variety of liquid pressurizer and distributor ensemblescan be implemented that are suitable for incorporation in a number ofthe above-described robust air conditioning systems in accordance withmany embodiments of the invention.

Cold Thermal Energy Storage Units for Implementation Within Robust AirConditioning Systems

In many embodiments, cold thermal energy storage units are implementedthat are suitable to be incorporated within many of the above describedair conditioning system configurations.

For example, FIGS. 12A-12C illustrate a configuration for and operationof a cold thermal store (in general, within the context of the instantapplication, the terms “thermal store” and “thermal energy storage unit”are synonymous) of robust air conditioning systems. In operation, a coldthermal store of a robust air conditioning systems can function in thethree distinct modes of being unused, charging, and dischargingrepresented by FIG. 12A, 12B and 12C respectively.

In particular, FIG. 12A illustrates the configuration of a cold thermalstore 1200 which includes a cold storage medium 1202 and an expansiondevice 1204, all of which are operatively interconnected by piping. Asis the case with all figures, although not depicted, valves can beincorporated to facilitate the operation of the cold thermal store 1200in accordance with many embodiments of the invention.

The cold storage medium 1202 generally operates to store thermalpotential in the sensible or latent heat of an embedded material.Although the cold storage medium 1202 is depicted schematically itshould be appreciated that it can be implemented using any of a varietyof schemes. For example, in many embodiments, the cold storage medium1202 comprises a heat exchanger in thermal contact with an embeddedphase change material. In another scheme, the cold storage medium 1202comprises an insulated bulk material through which circulatingrefrigerant can directly pass. Of course, to be clear, a cold thermalstore can be effectuated in any of a variety of ways in accordance withembodiments of the invention.

The expansion device 1204 generally operates to expand a higher pressurefluid to a lower pressure. Although the expansion device 1204 isdepicted schematically it should be appreciated that it can beimplemented using any of a variety of schemes. For example, in manyembodiments, the expansion device 1204 comprises an electronic expansionvalve. In another scheme, the expansion device 1204 comprises a turbine.In any case, it should be clear that any suitable device can be used asan expansion device in accordance with embodiments of the invention.

FIG. 12B illustrates how the cold thermal store 1200 can operate tostore thermal potential for later use. In particular, the bolded lines(and arrows) depict the circulation of a working fluid so as to directfluid to cool the cold storage medium 1202. More specifically, in theillustrated embodiment, the expansion device 1204 acts to expandincoming high pressure liquid phase working fluid (e.g. from a liquidpressurizer/distributor ensemble or the like) to a lower pressure andtemperature. The working fluid then passes into the cold storage medium1202 which is cooled as the working fluid absorbs heat and isevaporated. The low pressure, low temperature gas then passes out ofcold thermal store 1200 (e.g. to a suction gas equalizer/distributorensemble or the like).

FIG. 12C illustrates how the cold thermal store 1200 can operate torelease stored thermal potential on demand. In particular, the boldedlines (and arrows) depict the circulation of a working fluid so as torelease the stored thermal potential in the cold storage medium 1202 andprovide condensed liquid working fluid (e.g. to a liquidpressurizer/distributor ensemble or the like). More specifically, in theillustrated embodiment, cold low pressure gas working fluid enters thecold storage medium 1202 (e.g from a suction gas equalizer/distributorensemble or the like) and is condensed into a low pressure liquid whichthen leaves the cold thermal store 1200. Though not depicted, othersuitable components such as receivers, valves, and sensors can be addedwithout departing from the scope of the cold thermal store 1200 inaccordance with many embodiments.

FIGS. 13A-13C illustrate a configuration for and operation of a coldthermal store employing two stage expansion of robust air conditioningsystems. In operation, a cold thermal store employing two stageexpansion can function in the three distinct modes of being unused,charging, and discharging represented by FIG. 13A, 13B and 13Crespectively.

In particular, FIG. 13A illustrates the configuration of a cold thermalstore 1300. More specifically, the structure of the cold thermal store1300 is similar to that seen with respect to FIG. 12A, insofar as itincludes: a cold storage medium 1302 and an expansion device 1304. Thecold thermal store 1300 further includes a second expansion device 1308and a liquid gas separator 1306 that can separate a mixed phase flowinto its constituent liquid and gas phases with some effectiveness.Components are operatively interconnected by piping in accordance withmany embodiments. Though not depicted, other suitable components such asreceivers, flow control valves, sensors and circulation devices can beadded without departing from the scope of the cold thermal store 1300 inaccordance with many embodiments.

FIG. 13B illustrate the operation of the cold thermal store 1300 tostore thermal potential for later use. In particular, the bolded lines(and arrows) depict the circulation of a working fluid so as to directfluid (i.e. from a liquid pressurizer/distributor ensemble or the like)to cool the cold storage medium 1302. More specifically, in theillustrated embodiment, the expansion device 1304 acts to expandincoming liquid phase working fluid that is high pressure into a lowerpressure and temperature. The likely mixed phase working fluid is thenseparated into liquid and gas streams. The gas stream exits at anintermediate pressure (i.e. to a suction gas equalizer/distributorensemble or the like). The remaining liquid is expanded again by thesecond expansion device 1308 to a lower pressure and temperature. Theworking fluid then passes into the cold storage medium 1302 which iscooled as the working fluid absorbs heat and is evaporated. The lowpressure, low temperature gas then passes out of cold thermal store 1300via a separate line at a lower pressure (i.e. to a suction gasequalizer/distributor ensemble or the like).

FIG. 13C illustrates how the cold thermal store 1300 can operate torelease stored thermal potential on demand. In particular, the boldedlines (and arrows) depict the circulation of a working fluid so as torelease the stored thermal potential in the cold storage medium 1302 andprovide condensed liquid working fluid (i.e. to a liquidpressurizer/distributor ensemble). More specifically, in the illustratedembodiment, cold low pressure gas working fluid enters the cold storagemedium 1302 (e.g. from a suction gas equalizer/distributor ensemble) andis condensed into a low pressure liquid which then leaves the coldthermal store 1300.

FIGS. 14A-14C illustrate a configuration for and operation of a coldthermal store employing two stage expansion and a secondary heattransfer fluid of robust air conditioning systems incorporating coldthermal energy storage devices. In operation, a cold thermal storeemploying two stage expansion and a secondary heat transfer fluid canfunction in the three distinct modes of being unused, charging, anddischarging represented by FIG. 14A, 14B and 14C respectively.

In particular, FIG. 14A illustrates the configuration of a cold thermalstore 1400. More specifically, the structure of the cold thermal store1400 is similar to that seen with respect to FIG. 13A, insofar as itincludes: two expansion devices 1404 and 1408, and a liquid gasseparator 1406. The cold thermal store 1400 further includes a primaryheat exchanger 1402, a suction line heat exchanger 1410, a thermalenergy store 1412, and a circulation pumping device 1414. The expansiondevices 1404 and 1408, the liquid gas separator 1406, the suction lineheat exchanger 1410 and the primary heat exchanger 1402 are operativelyconnected by piping and are thermally connected via the primary heatexchanger 1402 to a second loop comprising the primary heat exchanger1402, the thermal energy store 1412 and a circulation pumping device1414. As is the case with all figures, although not depicted, valves andother inline components can be incorporated to facilitate the operationof the cold thermal store 1400 in accordance with many embodiments ofthe invention. Of course, to be clear, a cold thermal store 1400 can beeffectuated in any of a variety of ways in accordance with embodimentsof the invention.

The primary heat exchanger 1402 generally operates to transfer heatbetween the working fluid and a secondary heat transfer fluid. Althoughthe primary heat exchanger 1402 is depicted schematically it should beappreciated that it can be implemented using any of a variety ofschemes. For example, in many embodiments, the primary heat exchanger1402 comprises a brazed plate heat exchanger. In another scheme, theprimary heat exchanger 1402 comprises a shell and tube heat exchanger.In any case, it should be clear that any suitable heat exchanging devicecan be used as a primary heat exchanger in accordance with embodimentsof the invention.

The suction line heat exchanger 1410 generally operates to transfer heatbetween liquid phase working fluid and vapor phase working fluid.Although the suction line heat exchanger 1410 is depicted schematicallyit should be appreciated that it can be implemented using any of avariety of schemes. For example, in many embodiments, the suction lineheat exchanger 1410 comprises a brazed plate heat exchanger. In anotherscheme, the suction line heat exchanger 1410 comprises a spiral heatexchanger. In any case, it should be clear that any suitable heatexchanging device can be used as a suction line heat exchanger inaccordance with embodiments of the invention.

The thermal energy store 1412 is similar to the cold storage medium 1302as seen in FIGS. 13A-13C in that it serves a similar function as theprimary means for the storage of thermal potential, however it isdifferent in that it is in primary thermal communication with asecondary heat transfer fluid other than the system working fluid.Although the thermal energy store 1412 is depicted schematically itshould be appreciated that it can be implement using any of a variety ofschemes. For example, in many embodiment, the thermal energy store 1412comprises a tank filled with a phase change material in thermalcommunication with coils capable of carrying any number of secondaryheat transfer fluids. In another scheme, the thermal energy store 1412comprises a tank full of capsules filled with a phase changing materialwhere by the secondary heat transfer can percolate through the matrix.In yet another scheme, the thermal energy store 1412 is an insulatedtank that can hold a solid phase of the secondary heat transfer fluidwhile allowing the liquid phase to pass through.

FIG. 14B illustrates the operation of the cold thermal store 1400 tostore thermal potential for later use. In particular, the bolded lines(and arrows) depict the circulation of a working fluid so as to directfluid (i.e. from a liquid pressurizer/distributor ensemble) to cool thethermal energy store 1412. As in FIG. 13B, working fluid goes through atwo stage expansion process to transfer cooling to the thermal energystore 1412. Unlike in 13B, the heat is transferred through the primaryheat exchanger from a secondary heat transfer loop that is connected tothe thermal energy store 1412.

FIG. 14C illustrates how the cold thermal store 1400 can operate torelease stored thermal potential on demand. In particular, the boldedlines (and arrows) depict the circulation of a working fluid so as torelease the stored thermal potential in the cold storage medium 1402 andprovide condensed liquid working fluid (i.e. to a liquidpressurizer/distributor ensemble). More specifically, in the illustratedembodiment, cold low pressure gas working fluid enters the primary heatexchanger 1402 (e.g. from a suction gas equalizer/distributor ensemble)and is condensed into a low pressure liquid which then leaves the coldthermal store 1400. The heat from the incoming vapor phase refrigerantis absorbed by a secondary heat transfer fluid in the primary heatexchanger 1402 in thermal communication with the thermal energy store1412.

FIGS. 15A-15C illustrate a configuration for and operation of a coldthermal store employing a cascade vapor compression cycle of robust airconditioning systems incorporating cold thermal energy storage devices.In operation, a cold thermal store employing a cascade vapor compressioncycle can function in the three distinct modes of being unused,charging, and discharging represented by FIG. 15A, 15B and 15Crespectively.

In particular, FIG. 15A illustrates the configuration of a cold thermalstore 1500. More specifically, the structure of the cold thermal store1500 is similar to that seen with respect to FIG. 14A, insofar as itincludes: expansion devices 1504 and 1506, a primary heat exchanger1502, a circulation pumping device 1510 and a thermal energy store 1512.The cold thermal store 1500 further includes a compressor 1508. Theexpansion device 1504 and the primary heat exchanger 1502 areoperatively connected by piping and are thermally connected via theprimary heat exchanger 1502 to a second loop comprising the primary heatexchanger 1502, the thermal energy store 1512, a compressor 1508 and anexpansion device 1506 piped to implement a vapor compression cycle. Inaddition, the circulation pumping device 1510 is piped in parallel withthe expansion device and the compressor 1508 can be bypassed via apiping pathway. As is the case with all figures, although not depicted,valves and other inline components can be incorporated to facilitate theoperation of the cold thermal store 1500 and, a cold thermal store 1500can be effectuated in any of a variety of ways in accordance withembodiments of the invention.

FIG. 15B illustrates the operation of the cold thermal store 1500 tostore thermal potential for later use. In particular, the bolded lines(and arrows) depict the circulation of a working fluid so as to directfluid (i.e. from a liquid pressurizer/distributor ensemble) to cool thethermal energy store 1512. As depicted in FIG. 15B, high pressure liquidworking fluid (i.e. from a liquid pressurizer/distributor or the like)is expanded by the expansion device 1504 to a low pressure fluid, isevaporated in the primary heat exchanger 1502 and exits the cold thermalstore 1500 (i.e. to a suction gas equalizer/distributor). In this waythe primary heat exchanger 1502 operates as a condenser for a secondaryworking fluid circuit that is piped as to enable a vapor compressioncycle consisting of the compressor 1508, an expansion device 1506 andthe thermal energy store 1512 acting as the evaporator. The secondaryworking fluid vapor compression cycle allows the thermal energy store1512 to be cooled to a lower temperature than the evaporationtemperature of the primary working fluid.

FIG. 15C illustrates how the cold thermal store 1500 can operate torelease stored thermal potential on demand. In particular, the boldedlines (and arrows) depict the circulation of a working fluid so as torelease the stored thermal potential in the thermal energy store 1512and provide condensed liquid working fluid (i.e. to a liquidpressurizer/distributor ensemble). More specifically, in the illustratedembodiment, cold low pressure gas working fluid enters the primary heatexchanger 1502 (e.g. from a suction gas equalizer/distributor ensemble)and is condensed into a low pressure liquid which then leaves the coldthermal store 1500. The heat from the incoming vapor phase refrigerantis absorbed by a secondary working fluid which changes phase from a coldliquid to a vapor in the primary heat exchanger 1502. The secondaryworking fluid vapor bypasses the compressor 1508 and travels to thethermal energy store 1512 where it is condensed into a liquid and ispumped back to the primary heat exchanger 1502 while bypassing theexpansion device 1506 and completing the circuit.

FIGS. 16A-16C illustrate a configuration for and operation of a coldthermal store employing a cascade vapor compression cycle and asecondary heat transfer loop of robust air conditioning systemsincorporating cold thermal energy storage devices. In operation, a coldthermal store employing a cascade vapor compression cycle and asecondary heat transfer loop can function in the three distinct modes ofbeing unused, charging, and discharging represented by FIG. 16A, 16B and16C respectively.

In particular, FIG. 16A illustrates the configuration of a cold thermalstore 1600. More specifically, the structure of the cold thermal store1600 is similar to that seen with respect to FIG. 15A, insofar as itincludes: expansion devices 1604 and 1606, a primary heat exchanger1602, a circulation pumping device 1614, a compressor 1608 and a thermalenergy store 1612. The cold thermal store 1600 further includes acharging heat exchanger 1610 and a discharging heat exchanger 1616. Theexpansion device 1604 and the primary heat exchanger 1602 areoperatively connected by piping and are thermally connected via theprimary heat exchanger 1602 to a second loop using a secondary workingfluid comprising the primary heat exchanger 1602, a compressor 1608, anexpansion device 1606 and a charging heat exchanger 1610 piped toimplement a vapor compression cycle. In addition, the charging heatexchanger 1610 is in thermal communication with a thermal energy store1612 and a discharging heat exchanger 1616 via a third heat transferfluid which can be motivated by a circulation pumping device 1614. As isthe case with all figures, although not depicted, valves and otherinline components can be incorporated to facilitate the operation of thecold thermal store 1600 and, a cold thermal store 1600 can beeffectuated in any of a variety of ways in accordance with embodimentsof the invention.

FIG. 16B illustrates the operation of the cold thermal store 1600 tostore thermal potential for later use. In particular, the bolded lines(and arrows) depict the circulation of a working fluid so as to directfluid (i.e. from a liquid pressurizer/distributor ensemble) to cool thethermal energy store 1612. As depicted in FIG. 16B, high pressure liquidworking fluid (i.e. from a liquid pressurizer/distributor or the like)is expanded by the expansion device 1604 to a low pressure fluid, isevaporated in the primary heat exchanger 1602 and exits the cold thermalstore 1600 (i.e. to a suction gas equalizer/distributor). In this waythe primary heat exchanger 1602 operates as a condenser for a secondaryworking fluid circuit that is piped as to enable a vapor compressioncycle consisting of the compressor 1608, an expansion device 1606 andthe charging heat exchanger 1610 acting as the evaporator. The chargingheat exchanger is in thermal communication with the thermal energy store1612 via a third heat transfer fluid loop and is used to cool thethermal energy store. The secondary working fluid vapor compressioncycle allows the third heat transfer fluid loop to be cooled to a lowertemperature than the evaporation temperature of the primary workingfluid.

FIG. 16C illustrates how the cold thermal store 1600 can operate torelease stored thermal potential on demand. In particular, the boldedlines (and arrows) depict the circulation of a working fluid so as torelease the stored thermal potential in the thermal energy store 1612and provide condensed liquid working fluid (i.e. to a liquidpressurizer/distributor ensemble). More specifically, in the illustratedembodiment, cold low pressure gas working fluid enters the primary heatexchanger 1602 (e.g. from a suction gas equalizer/distributor ensemble)and is condensed into a low pressure liquid which then leaves the coldthermal store 1600. The heat from the incoming vapor phase refrigerantis absorbed by thermal energy store 1612 and is transferred by the thirdheat transfer fluid via the discharging heat exchanger 1616.

FIGS. 17A-17C illustrate a configuration for and operation of a coldthermal store employing a stand-alone charging vapor compression cycleand a secondary heat transfer loop of robust air conditioning systemsincorporating cold thermal energy storage devices. In operation, a coldthermal store employing a stand-alone vapor compression cycle and asecondary heat transfer loop can function in the three distinct modes ofbeing unused, charging, and discharging represented by FIG. 17A, 17B and17C respectively.

In particular, FIG. 17A illustrates the configuration of a cold thermalstore 1700. More specifically, the structure of the cold thermal store1700 is similar to that seen with respect to FIG. 16A, insofar as itincludes: an expansion device 1710, a primary heat exchanger 1702, acirculation pumping device 1706, a thermal energy store 1704, acompressor 1708 and a charging heat exchanger 1714. The cold thermalstore 1700 further includes a condenser 1712. The primary heat exchanger1702 is connected to an inlet and out let of the cold thermal store 1700and connects to a secondary heat transfer loop that is in thermalcommunication with the thermal energy store 1704 and a charging heatexchanger 1714 where by the secondary heat transfer fluid can bemotivated by a circulation pumping device 1706. Finally the chargingheat exchanger 1714 is connected to a stand-alone vapor compressioncycle utilizing a third working fluid and consisting of a compressor1708, a condenser 1712 and an expansion device 1710. As is the case withall figures, although not depicted, valves and other inline componentscan be incorporated to facilitate the operation of the cold thermalstore 1700 and, a cold thermal store 1700 can be effectuated in any of avariety of ways in accordance with embodiments of the invention.

FIG. 17B depicts the operation of the cold thermal store 1700 to storethermal potential for later use. As depicted in FIG. 17B no workingfluid is taken in by the cold thermal store 1700 during charging.Instead, a working fluid is circulated through a stand-alone vaporcompression cycle that rejects heat from the thermal energy store 1704via the charging heat exchanger 1714 that is in thermal communicationwith the thermal energy store via a secondary heat transfer fluid. Thestand-alone vapor compression cycle allows the thermal energy store 1704to be charged at any appropriate temperature for the operation of thecold thermal store 1700.

FIG. 17C illustrates how the cold thermal store 1700 can operate torelease stored thermal potential on demand. In particular, the boldedlines (and arrows) depict the circulation of a working fluid so as torelease the stored thermal potential in the thermal energy store 1704and provide condensed liquid working fluid (i.e. to a liquidpressurizer/distributor ensemble). More specifically, in the illustratedembodiment, cold low pressure gas working fluid enters the primary heatexchanger 1702 (e.g. from a suction gas equalizer/distributor ensemble)and is condensed into a low pressure liquid which then leaves the coldthermal store 1700. The heat from the incoming vapor phase refrigerantis absorbed by the thermal energy store 1704 and is transferred from theprimary heat exchanger 1702 by the secondary heat transfer fluid.

While several examples of cold thermal stores that are suitable forimplementation within many of the above described robust airconditioning systems are described, it can be appreciated that any of avariety of cold thermal stores can be implemented that are suitable forincorporation in a number of the above-described robust air conditioningsystems in accordance with many embodiments of the invention.

Suction Gas Pressurizer And Distributor Ensembles for ImplementationWithin Robust Air Conditioning Systems

In many embodiments, suction gas pressurizer and distributor ensemblesare implemented that are suitable to be incorporated within many of theabove described air conditioning system configurations.

FIG. 18 depicts a configuration of a suction gas equalizer/distributor1800 that can accept two streams of vapor phase working fluid atdifferent pressures from a cold thermal store as well as multiplestreams from target spaces and equalizes them to a common suction gaspressure via an expansion valve 1802 for the cold thermal store andexpansion valves 1804, 1806, 1808 and 1810 for the target spaces. Duringcold thermal store discharge mode, low pressure suction gas bypasses theexpansion valve 1802 as it exits the suction gas equalizer/distributor1800. As can be appreciated, although not depicted, valves or otherinline components can be incorporated to facilitate the operation of thesuction gas equalizer/distributor 1800 in accordance with manyembodiments of the invention.

FIG. 19 depicts a configuration of a suction gas equalizer/distributor1900 that can accept two streams of vapor phase working fluid atdifferent pressures from a cold thermal store and equalize the lowerpressure stream to the same pressure as the multiple inlet streams fromtarget spaces and higher pressure stream from the cold thermal store viaa booster compressor 1902. During cold thermal store discharge mode, lowpressure suction gas bypasses the booster compressor 1902 as it exitsthe suction gas equalizer/distributor 1900. As can be appreciated,although not depicted, valves or other inline components can beincorporated to facilitate the operation of the suction gasequalizer/distributor 1900 in accordance with many embodiments of theinvention.

While several examples of suction gas equalizer and distributors thatare suitable for implementation within many of the above describedrobust air conditioning systems are described, it can be appreciatedthat any of a variety of suction gas equalizer and distributors can beimplemented that are suitable for incorporation in a number of theabove-described robust air conditioning systems in accordance with manyembodiments of the invention.

Hot Thermal Energy Storage Units for Implementation Within Robust AirConditioning Systems

In many embodiments, hot thermal energy storage units are implementedthat are suitable to be incorporated within many of the above describedair conditioning system configurations.

FIG. 20 illustrates a configuration of a hot thermal store of robust airconditioning systems incorporating cold and hot thermal energy storagedevices. In particular, FIG. 20 illustrates the configuration of a hotthermal store 2000 which includes a heat exchanger 2002, a thermalenergy store 2004, and a circulation pumping device 2006 which areoperatively connected by piping. In operation, as hot high pressurevapor phase working fluid enters the hot thermal store 2000 (i.e. fromthe discharge gas distributor) it travels through the heat exchanger2002 and is condensed into high pressure liquid. During the condensationprocess heat is rejected by the working fluid into the thermal energystore 2004 which is in thermal communication via a circulating secondaryheat transfer fluid. During discharge of the hot thermal store 2000,high pressure liquid working fluid enters the heat exchanger 2002 (i.e.from the liquid pressurizer/distributor ensemble or the like) and isboiled by the thermal store which is in thermal communication via thesecondary heat transfer media. As is the case with all figures, althoughnot depicted, valves and other components can be incorporated tofacilitate the operation of the hot thermal store 2000 in accordancewith many embodiments of the invention.

While an example of a hot thermal energy storage unit that is suitablefor implementation within many of the above described robust airconditioning systems is described, it can be appreciated that any of avariety of hot thermal energy storage units can be implemented that aresuitable for incorporation in a number of the above-described robust airconditioning systems in accordance with many embodiments of theinvention.

Configurations for Hot Thermal Storage Units That Can Also Act as a HeatSource for Implementation Within Robust Air Conditioning Systems

In many embodiments, hot thermal energy storage units that can alsofunction as heat sources are implemented that are suitable to beincorporated within many of the above described air conditioning systemconfigurations.

For example, FIG. 21 illustrates a configuration of a heat source ofrobust air conditioning systems incorporating cold and hot thermalenergy storage devices. In particular, FIG. 21 illustrates theconfiguration of a heat source 2100 which includes a heat exchanger 2102and a heating element 2104. In operation, during discharge high pressureliquid phase working fluid travels through the heat exchanger 2102 andis boiled by the heating element 2104. The resulting high pressure vaporphase working fluid leaves the heat source 2100 (i.e. to the dischargegas distributor or the like). As is the case with all figures, althoughnot depicted, valves and other components can be incorporated tofacilitate the operation of the heat source 2100 in accordance with manyembodiments of the invention.

The heating element 2104 of the heat source 2100 provides heat to boilliquid working fluid. Although the heating element 2104 is depictedschematically it should be appreciated that it can be implemented usinga variety of schemes. For example, in many embodiments, the heat source2104 comprises as gas burner. In another scheme, the heat source 2104comprises a bioreactor containing an exothermic reaction. Of course, tobe clear, a heating element and heat source can be effectuated in any ofa variety of ways in accordance with embodiments of the invention.

While an example of a hot thermal energy storage unit that can alsoserve as a heat source and that is suitable for implementation withinmany of the above described robust air conditioning systems isdescribed, it can be appreciated that any of a variety of hot thermalenergy storage units that can also serve as heat sources can beimplemented that are suitable for incorporation within in a number ofthe above-described robust air conditioning systems in accordance withmany embodiments of the invention.

Alternative Robust Air Conditioning System Configurations

In many embodiments, alternative robust air conditioning systemconfigurations are implemented.

For example, FIGS. 22A-22C illustrate a multiple connected configurationfor and operation of robust air conditioning systems incorporating bothhot and cold thermal energy storage units. In operation the multipleconnected configuration can function in a similar manner as a robust airconditioning system that includes separate thermal energy storage unitsfor heating and cooling a target space as depicted in FIGS. 3A-3K.

In particular FIG. 22A illustrate that the air conditioning system 2200is similar to that seen in FIG. 3A insofar as it includes: condensingunits 2202, target spaces 2204, liquid pressurizer/distributor ensembles2206, cold thermal energy storage units 2208, suction gasconditioner/distributors 2210, hot thermal energy storage units 2212 anddischarge gas distributors 2214. FIG. 22A further depicts a unifiedcondenser 2216, a unified cold thermal energy store 2218, a unified hotthermal energy store 2220, circulation pumps 2222 and individual entirerobust air conditioning systems incorporating both hot and cold thermalenergy storage units 2224.

The air condition system 2200 as depicted in FIG. 22A is comprised ofmultiple robust air condition systems 2224 as depicted in FIG. 3A wherein the cold thermal stores 2208 have been configured to share oneunified cold thermal energy store 2218, the hot thermal stores 2212 havebeen configured to share one unified hot thermal energy store 2220 andthe condensing units 2202 have been configured to share one condenser2216. In many embodiments, all three unified connections are made bysecondary heat transfer fluid loops in which the heat transfer fluid ismotivated by circulation pumps 2222. In many embodiments, the unifiedconnections are made by loops filled with the primary working fluid. Asis the case with all figures, although not depicted, valves can beincorporated to facilitate the operation of the air conditioning system2200 in accordance with many embodiments of the invention.

FIG. 22B depicts the air conditioning system 2200 in an operational modein which the unified cold thermal energy store 2218 and the unified hotenergy store 2220 are being charge by the condensing units 2202 of thevarious individual entire robust air conditioning systems 2224 using ashared condenser 2216.

FIG. 22C depicts the air condition system 2200 in an operational mode inwhich the unified cold thermal energy store 2218 and the unified hotenergy store 2220 are being used in conjunction with the variousindividual entire robust air conditioning systems 2224 to providecooling and/or heating to the target spaces 2204.

FIGS. 23A-23C illustrate a multiple connected configuration for andoperation of robust air conditioning systems incorporating cold thermalenergy storage devices operable to provide cooling and/or heatingservices. In operation the multiple connected configuration can functionin a similar manner as robust air conditioning systems incorporatingcold thermal energy storage devices operable to provide cooling and/orheating services as depicted in FIGS. 2A-2I.

In particular FIG. 23A illustrate that the air conditioning system 2300is similar to that seen in FIG. 22A insofar as it includes: condensingunits 2302, target spaces 2304, liquid pressurizer/distributor ensembles2306, cold thermal energy storage unit 2308, a suction gasconditioner/distributor 2310, a unified cold thermal energy store 2312,circulation pumps 2314, a unified condenser 2318. FIG. 23A furtherdepicts a unified integrated heating source 2316 on a shared connectionwith the unified condenser 2318. An individual entire robust airconditioning systems incorporating cold thermal energy storage devicesoperable to provide cooling and/or heating services 2320 is alsodepicted. Though not depicted, other suitable components such asreceivers, valves, and sensors can be added without departing from thescope of the air conditioning system 2300 in accordance with manyembodiments.

FIG. 23B depicts the air conditioning system 2300 in an operational modein which the unified cold thermal energy store 2312 is being charge bythe condensing units 2302 of the various individual entire robust airconditioning systems 2320 using a unified condenser 2318.

FIG. 23C depicts the air condition system 2300 in an operational mode inwhich the unified cold thermal energy store and the unified integratedheating source 2316 is being used in conjunction with the variousindividual entire robust air conditioning systems 2320 to providecooling and/or heating to the target spaces 2304. Of course, to beclear, the air condition system 2300 can be effectuated in any of avariety of ways in accordance with embodiments of the invention.

While several alternative configurations for robust air conditioningsystems have been depicted, it should be clear that any of a variety ofrobust air conditioning system configurations can be implemented inaccordance with many embodiments of the invention.

More generally, as can be inferred from the above discussion, theabove-mentioned concepts can be implemented in a variety of arrangementsin accordance with embodiments of the invention. Accordingly, althoughthe present invention has been described in certain specific aspects,many additional modifications and variations would be apparent to thoseskilled in the art. It is therefore to be understood that the presentinvention may be practiced otherwise than specifically described. Thus,embodiments of the present invention should be considered in allrespects as illustrative and not restrictive.

What claimed is:
 1. An air conditioning system comprising: a condensingunit; a liquid pressurizer and distributor ensemble; a cold thermalenergy storage unit; a target space; and a suction gas pressurizer anddistributor ensemble; wherein: the condensing unit, the liquidpressurizer and distributor ensemble, the cold thermal energy storageunit, the target space, and the suction gas pressurizer and distributerensemble are operatively connected by piping such that vapor compressioncycles can be simultaneously implemented that result in the cooling ofthe cold thermal energy storage unit and the target space; and the airconditioning system is configured such that when the vapor compressioncycles are simultaneously implemented that result in the cooling of thecold thermal energy storage unit and the target space, the cold thermalenergy storage unit cools to a greater extent than the target space. 2.The air conditioning system of claim 1, wherein: the cold thermal energystorage unit comprises a first expansion device; the target spacecomprises a second expansion device; and the first expansion device isoperable to reduce the temperature of received working fluid to agreater extent than the second expansion device.
 3. The air conditioningsystem of claim 1, wherein the suction gas pressurizer and distributorensemble comprises: at least one of: a pressure regulator and acompressor; and a flow control apparatus operable to controllably directvapor phase working fluid to adjoined structures.
 4. The airconditioning system of claim 1, wherein the cold thermal energy storageunit comprises a phase change material encased in thermal insulation. 5.The air conditioning system of claim 1, wherein the condensing unitcomprises a compressor and condenser in series, and wherein thecondensing unit is operable to direct received vapor phase working fluidthrough a compressor to compress the vapor phase working fluid, and thendirect the compressed vapor phase working fluid through a condenser tocondense the vapor phase working fluid, such that the condensing unitcan output the corresponding liquid phase working fluid.
 6. The airconditioning system of claim 1, wherein the liquid pressurizer anddistributor ensemble comprises a pump that is operable to alter thepressure of received liquid phase working fluid, and a flow controlapparatus operable to controllably direct received liquid phase workingfluid to adjoined structures. The air conditioning system of claim 1,wherein the condensing unit is operable to output heated vapor phaseworking fluid.
 8. The air conditioning system of claim 7, wherein thecondensing unit comprises an integrated heating source and is therebyoperable to output heated vapor phase working fluid.
 9. The airconditioning system of claim 8, wherein the integrated heating source isa gas powered heater.
 10. The air conditioning system of claim 7,further comprising piping configured to direct heated vapor phaseworking fluid that is output by the condensing unit to the target space.11. The air conditioning system of claim 10, wherein the condensing unitis configured to output heated vapor phase working fluid such that whenthe heated vapor phase working fluid is directed by the piping to thetarget space, it condenses into a liquid phase working fluid.
 12. Theair conditioning system of claim 7, further comprising: a discharge gasdistributor; and a hot thermal energy storage unit; wherein thedischarge gas distributor, the hot thermal energy storage unit, theliquid pressurizer and distributor ensemble, and the target space areoperatively connected by piping such that heated vapor phase workingfluid output by the condensing unit can be circulated, using thedischarge gas distributor, to the target space and/or the hot thermalenergy storage unit.
 13. The air conditioning system of claim 12,wherein the condensing unit is configured to output heated vapor phaseworking fluid such that when the heated vapor phase working fluid isdirected by piping to the target space and/or the hot thermal energystorage unit, it condenses into a liquid phase working fluid.
 14. Theair conditioning system of claim 13, wherein the hot thermal energystorage unit comprises a thermal storage medium encased in thermalinsulation.
 15. The air conditioning system of claim 12, furthercomprising: a second condensing unit; a second liquid pressurizer anddistributor ensemble; a second target space; a second discharge gasdistributor; and a condenser; wherein: the condensing unit and thesecond condensing unit are operatively connected by piping to thecondenser; the second condensing unit, the second liquid pressurizer anddistributor ensemble, the second target space, and the cold thermalenergy storage unit are operatively connected by piping such that vaporcompression cycles can be simultaneously implemented that result in thecooling of the cold thermal energy storage unit and the target space;and the second condensing unit, the second discharge gas distributor,the second target space, and the hot thermal energy storage unit areoperatively connected by piping such that a working fluid can be heatedand circulated through the target space to heat it.
 16. The airconditioning system of claim 1, further comprising: a hot thermal energystorage unit that is operable to act as a heat source; wherein: the hotthermal energy storage unit and the target space are operativelyconnected by piping; and the hot thermal energy storage unit isconfigured to receive liquid phase working fluid, and heat it so that itoutputs vapor phase working fluid that thereafter be directed to thetarget space to heat it.
 17. The air conditioning system of claim 16,wherein the air conditioning system is configured such that the vaporphase working fluid that is output by the hot thermal energy storageunit and thereafter directed to the target space, transmits heat to thetarget space and thereby condenses.
 18. The air conditioning system ofclaim 1, wherein the condensing unit is configured to be operable onlyon received vapor phase working fluid that is within a distinct pressurerange, and the suction gas pressurizer and distributor ensemble isconfigured to output vapor phase working fluid that is within thedistinct pressure range.
 19. The air conditioning system of claim 1,wherein the cold thermal energy storage unit comprises a phase changematerial within a circuit that interfaces with the piping via a heatexchanger.
 20. The air conditioning system of claim 1, furthercomprising: a second condensing unit; a second liquid pressurizer anddistributor ensemble; a second target space; and a condenser; wherein:the condensing unit and the second condensing unit are operativelyconnected by piping to the condenser; and the second condensing unit,the second liquid pressurizer and distributor ensemble, the secondtarget space, and the cold thermal energy storage unit are operativelyconnected by piping such that vapor compression cycles can besimultaneously implemented that result in the cooling of the coldthermal energy storage unit and the target space.